JP7768264B2 - Ball screw device - Google Patents

Description

The present invention relates to a ball screw device.

A ball screw comprises a screw shaft, a nut, and multiple balls arranged between the screw shaft and the nut. In one example of a ball screw device, the rotational motion of the motor's output shaft is converted into linear motion by the ball screw. In ball screw devices, a bearing is generally installed between the ball screw and the housing to support the rotation of the ball screw (see, for example, Patent Document 1).

Japanese Patent Application Laid-Open No. 2004-284444

In ball screw devices with high load specifications, a known technology is to use a bearing capable of withstanding both radial and axial loads, such as a tapered roller bearing, between the ball screw and the housing. Ball screw devices that use bearings for radial loads, such as general ball bearings, require large-sized bearings that can withstand high loads, which tends to result in the device becoming larger. Ball screw devices that use bearings suitable for both radial and axial loads avoid the device becoming larger, even in high-load specifications.

However, in such ball screw devices, relative axial movement is likely to occur, for example, between the inner and outer rings of the bearings. Relative axial movement between the inner and outer rings can cause damage to the bearings, such as when the ends of the outer ring come into contact with the outer surfaces of the rolling elements. It can also cause abnormal noise in the ball screw device.

The object of the present invention is to provide a ball screw device that is suitable for use in high-load applications, has the advantage of being compact, and is highly reliable and has a long lifespan.

A ball screw device according to one aspect of the present invention comprises a ball screw having a screw shaft, a nut, and multiple balls; a housing supporting the ball screw; and a bearing having an inner ring, an outer ring, and multiple rolling elements. The bearing is disposed between the ball screw and the housing and is configured to support radial and axial loads. The housing has a first axial surface facing a first direction and a second axial surface facing a second direction. An axial load from the ball screw along the second direction is supported by the first axial surface via the inner ring, rolling elements, and outer ring. The bearing or the ball screw has a third axial surface disposed facing the second axial surface. When the screw shaft or the nut rotates relative to the housing, relative circumferential movement occurs between the second axial surface and the third axial surface. Relative axial movement of the inner ring in the first direction relative to the outer ring is restricted based on the axial positional relationship between the second axial surface and the third axial surface.

The ball screw device according to one aspect of the present invention can be preferably applied to high-load specifications, is advantageous for compactness, and provides a ball screw device with high reliability and a long lifespan.

1 is a schematic cross-sectional view showing a ball screw device according to a first embodiment. 1A is a diagram illustrating the contact angle α in a tapered roller bearing, and FIG. 1B is a diagram illustrating the contact angle α in an angular contact ball bearing. FIG. 2 is a diagram for explaining dimensional values of a tapered roller bearing. FIG. 2 is a schematic enlarged partial cross-sectional view showing the ball screw device according to the first embodiment. FIG. 10 is a schematic enlarged partial cross-sectional view showing a ball screw device according to a second embodiment. FIG. 10 is a schematic enlarged partial cross-sectional view showing a ball screw device according to a third embodiment. FIG. 11 is a schematic enlarged partial cross-sectional view showing a modified example of the third embodiment. FIG. 10 is a schematic, partially enlarged cross-sectional view showing a ball screw device according to a fourth embodiment. 10A, 10B, and 10C are schematic partially enlarged cross-sectional views showing ball screw devices according to fifth, sixth, and seventh embodiments, respectively. FIG. 19 is a schematic cross-sectional view showing a ball screw device according to an eighth embodiment. 13A, 13B, and 13C are schematic partially enlarged cross-sectional views showing ball screw devices according to eighth, ninth, and tenth embodiments, respectively. 13A, 13B, and 13C are schematic partially enlarged cross-sectional views showing ball screw devices according to 11th, 12th, and 13th embodiments, respectively.

Embodiments of the present invention will be described with reference to the drawings. In one embodiment, a ball screw device is incorporated into various mechanical devices, such as an electric brake device for a vehicle, an automatic manual transmission (AMT), or a positioning device for a machine tool, and is used to convert the rotational motion of a drive source such as an electric motor into linear motion to operate a driven part (operating part). Various types of electric brake devices are applicable, including an electro-mechanical brake (EMB) that applies braking force via a ball screw driven by a motor, and an electro-hydraulic brake (EHB) that controls the hydraulic pressure of a hydraulic brake via a ball screw driven by a motor. Ball screw devices can also be applied to mechanical devices other than those mentioned above.

In the following description, unless otherwise specified, the terms axial direction, radial direction, and circumferential direction refer to the direction along the central axis of the ball screw, the radial direction of the ball screw, and the direction around the central axis of the ball screw, respectively. Furthermore, the direction from the input side to the output side along the central axis of the ball screw is referred to as the first direction (first orientation), and the direction from the output side to the input side is referred to as the second direction (second orientation).

(First embodiment)
1 is a schematic cross-sectional view of a ball screw device 11 according to a first embodiment. The ball screw device 11 includes a ball screw 20, a housing 30 that supports the ball screw 20, and a bearing 40 that is disposed between the ball screw 20 and the housing 30.

As shown in FIG. 1, the ball screw 20 includes a screw shaft 21, a nut 22, and a plurality of balls 23 arranged between the screw shaft 21 and the nut 22. In one example, a first shaft 91, to which the driving force of a motor (not shown) is transmitted, is connected to the nut 22. The ball screw 20 converts rotational motion into linear motion. A reducer can also be additionally arranged between the ball screw 20 and the motor. In one example where the ball screw device 11 is applied to an electric brake device for a vehicle, the vehicle's brake pads operate against the brake disc in response to the linear motion. The ball screw 20 and the mechanism using it are not limited to this example, and various forms are applicable.

The screw shaft 21 has a shaft body and a spiral thread groove (spiral outer peripheral rolling groove) provided on the outer peripheral surface of the shaft body. In one example, at least a portion of the screw shaft 21 is made of metal. The thread groove of the screw shaft 21 is formed by cutting or rolling the outer peripheral surface of the shaft body. Grinding can be additionally performed in forming the thread groove. The thread groove shape (groove bottom shape) of the screw shaft 21 is, for example, a Gothic arch groove or a circular arc groove. The number of threads in the thread groove is set to one, two, or more. In other examples, various configurations are applicable to the screw shaft 21.

The nut 22 has a cylindrical nut body and a helical thread groove (helical inner peripheral rolling groove) provided on the inner surface of the nut body. The screw shaft 21 is inserted into the nut 22. In one example, at least a portion of the nut 22 is made of metal. The thread groove of the nut 22 is formed by cutting or rolling the inner surface of the nut body. Grinding can be additionally performed to form the thread groove. The thread groove shape (groove bottom shape) of the nut 22 corresponds to the groove shape of the screw shaft 21, and is, for example, a Gothic arch groove or a circular arc groove. The number of threads in the thread groove is set to one, two, or more. In other examples, various shapes are applicable to the nut 22.

A plurality of balls 23 are arranged between the screw shaft 21 and the nut 22. The plurality of balls 23 are arranged in a space (rolling path) formed by the opposing arrangement of the screw grooves of the screw shaft 21 and the nut 22. In Figure 1, two balls 23 are indicated by two-dot chain lines. In reality, the ball screw 20 includes many balls 23. In one example, the plurality of balls 23 are made of metal (such as steel) or ceramic. The plurality of balls 23 roll within the rolling path as the screw shaft 21 and the nut 22 rotate relative to each other. In one example, the balls 23 return from the end point of the rolling path to the start point via a circulation path provided in the nut 22. The balls 23 arranged in the rolling path move while being subjected to a compressive load. The balls 23 arranged in the circulation path are pushed and moved by the subsequent balls 23. The start and end points of the rolling path change positions depending on the direction of relative displacement (direction of relative rotation) between the screw shaft 21 and the nut 22. In other examples, the ball screw 20 may have a different structure for circulating the balls 23.

The housing 30 supports the ball screw 20 via bearings 40 and the like. Various additional support structures can be applied to the housing 30. At least a portion of the ball screw 20 is enclosed by the housing 30. At least a portion of the ball screw 20 is disposed in the internal space of the housing 30. In one example, at least a portion of the housing 30 is made of metal. In another example, at least a portion of the housing 30 is made of a material other than metal. The housing 30 is fixed to a predetermined structure (not shown). In one example, the housing 30 has a substantially divided structure. The division position of the housing 30 is appropriately set in consideration of the assembly process. In another example, the housing 30 can have a different structure.

The bearing 40 has an inner ring 41, an outer ring 42, and a plurality of rolling elements 43 arranged between the inner ring 41 and the outer ring 42. The plurality of rolling elements 43 are held between the inner ring 41 and the outer ring 42 via a cage 45. The bearing 40 may additionally have a seal structure that seals in a lubricant.

In this embodiment, a bearing capable of bearing radial and axial loads is used as the bearing 40. For example, the bearing 40 is a single-row tapered roller bearing or a single-row angular contact ball bearing. In one example, the bearing 40 is a single-row tapered roller bearing, and rollers (tapered rollers) are used as the rolling elements 43. In another example, the bearing 40 is a single-row angular contact ball bearing, and balls are used as the rolling elements 43. Tapered roller bearings have a higher load capacity than angular contact ball bearings. Angular contact ball bearings are more preferably used for high-speed rotation specifications than tapered roller bearings. The use of such a single bearing (a configuration that avoids a configuration in which two bearings are opposed to each other or a configuration in which two or more bearings are combined) is advantageous for making the ball screw device 11 more compact. Alternatively, other types of bearings can be used.

Typically, tapered roller bearings are designed so that the raceway surface of the inner ring, the raceway surface of the outer ring, and the apex of the roller cone substantially converge at a single point on the bearing's central axis. The rollers have a roughly truncated conical shape. Tapered roller bearings are capable of withstanding radial loads and unidirectional axial loads. In one example, the rollers are held in place by a stamped steel cage or a plastic cage. In another example, the rollers are held in place by a pin-type cage or another structure.

Angular contact ball bearings are generally designed so that the line connecting the contact points between the outer ring and balls and the inner ring and balls is inclined relative to the radial direction of the bearing. Angular contact ball bearings can withstand radial loads and unidirectional axial loads. In one example, the balls are held in place by a stamped steel cage or a resin (e.g., polyamide) cage. In other examples, the balls are held in place by a different structure.

In tapered roller bearings and angular contact ball bearings, the contact angle α is appropriately set as shown in Figure 2. Bearings with a relatively small contact angle α generally have a relatively high load capacity for radial loads. Bearings with a relatively large contact angle α generally have a high load capacity for axial loads.

In this embodiment, the contact angle α (see FIG. 2(a)) of the tapered roller bearing used as the bearing 40 of the ball screw device 11 of FIG. 1 is set to, for example, approximately 10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20, 21, 22, 23, 24, 25, 26, 27, 28, 29, 30, 31, 32, 33, 34, or 35°. In one example, a tapered roller bearing with a contact angle of 20° or more is used in a ball screw device 11 with high load specifications. In another example, a tapered roller bearing with a contact angle of 25° or more is used in a ball screw device 11 with even higher load specifications. The above values are by way of example only and are not limiting.

In this embodiment, the contact angle α (see FIG. 2(b)) of the angular contact ball bearing used as the bearing 40 of the ball screw device 11 in FIG. 1 is set to, for example, approximately 10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20, 21, 22, 23, 24, 25, 26, 27, 28, 29, 30, 31, 32, 33, 34, 35, 36, 37, 38, 39, 40, 41, 42, 43, 44, or 45°. In one example, an angular contact ball bearing with a contact angle of 27° or 32° or more is used in a ball screw device 11 with high load specifications. The above values are merely examples and are not limiting.

In this embodiment, in the example of a single-row tapered roller bearing shown in Figure 3, where L is the axial width of the outer ring and a is the distance between the rolling elements and the end of the outer ring, a/L is set to approximately 1/20, 1/18, 1/16, 1/14, 1/12, 1/10, 1/8, or 1/6 or greater. In one example, a bearing with a/L of 1/10 or greater is used. By appropriately setting the correspondence between the value of a/L and the design value of the allowable axial clearance (gap 900, described below), problems such as damage to the bearing 40 and abnormal noise caused by relative axial movement are reliably prevented. The above values are merely examples and are not limiting.

Returning to FIG. 1 , in this embodiment, the inner ring 41 of the bearing 40 is attached to the nut 22 of the ball screw 20, and the outer ring 42 of the bearing 40 is attached to the housing 30. Additionally and/or alternatively, various structures can be applied that include a separate member (not shown) (such as a thrust collar, a C-shaped retaining ring, or annular plate) for supporting the axial position of the inner ring 41 relative to the nut 22. Similarly, various structures can be applied that include a separate member (not shown) (such as a thrust collar, a C-shaped retaining ring, or annular plate) for supporting the axial position of the outer ring 42 relative to the housing 30.

As shown in FIG. 4, the outer diameter of the bearing 40 is larger than the outer diameter of the nut 22. In another example, the outer diameter of the bearing 40 can be smaller than the outer diameter of the nut 22. In FIG. 4, the bearing 40 is positioned substantially radially outward of the nut 22. The nut 22 has outer surfaces 221, 222 facing radially outward. The outer surface (outer circumferential surface) 222 of the nut 22 has an outer diameter corresponding to the diameter of the hole in the bearing 40 (the inner diameter of the inner ring 41). The nut 22 and the bearing 40 (inner ring 41) are fitted together by inserting a portion of the nut 22 into the hole in the bearing 40 so that the outer surface 222 of the nut 22 and the inner surface (inner circumferential surface) 411 of the inner ring 41 face each other. The inner surface 411 of the bearing 40 (inner ring 41) is supported by the outer surface 222 of the nut 22. An appropriate interference or gap (loose fit) is provided in the fit between the nut 22 and the inner ring 41. In another example, a configuration in which the nut 22 and inner ring 41 are integrally formed can be applied.

In this embodiment, the nut 22 has an axial surface (axial wall surface) 225 facing the second direction. The axial surface 225 is located between the outer surfaces 221 and 222 in the radial direction, and has, for example, a surface perpendicular to the axial direction. The inner ring 41 of the bearing 40 has an axial surface (axial end surface) 415 facing the first direction. The axial surface 415 is located at the end of the inner ring 41 in the first direction in the axial direction, and has, for example, a surface perpendicular to the axial direction. The axial surface 415 is also located between the inner surface 411 and the outer surface 412 in the radial direction. The axial surface 225 of the nut 22 is positioned opposite the axial end surface 415 of the inner ring 41.

In this embodiment, the ball screw 20 or the bearing 40 includes a sliding member 50. The sliding member 50 is provided as a separate member from the main body (screw shaft main body/nut main body) of the ball screw 20 or the main body (inner ring/outer ring) of the bearing 40. The sliding member 50 is ring-shaped and has a first surface 501 facing a first direction and a second surface 502 facing a second direction. The sliding member 50 is disposed between the axial surface 225 of the nut 22 and the axial end surface 415 of the inner ring 41. The axial surface 225 of the nut 22 abuts against the first surface 501 of the sliding member 50. The axial end surface 415 of the inner ring 41 abuts against the second surface 502 of the sliding member 50. The sliding member 50 is fixed to the nut 22 and the inner ring 41 by being sandwiched between the nut 22 and the inner ring 41. The sliding member 50 is incorporated as part of the second assembly (inner assembly, rotating body) 70. The second assembly 70 is rotatably supported by the first assembly (outer assembly, support) 60. In this embodiment, the first assembly 60 includes a housing 30, an outer ring 42, etc. The second assembly 70 includes a nut 22, an inner ring 41, and a sliding member 50, etc. In one example, a member having a configuration similar to that of a sliding bearing is used as the sliding member 50. In another example, a member having a relatively simple configuration similar to that of a spacer is used as the sliding member 50.

As shown in FIG. 4, the housing 30 has inner surfaces (inner wall surfaces) 301, 302, and 303 that surround the ball screw 20. The inner surface (inner peripheral surface) 302 is disposed between the inner surfaces 301 and 303 in the axial direction. The inner surface 302 has an inner diameter that corresponds to the outer diameter of the bearing 40 (the outer diameter of the outer ring 42). The inner surfaces 301, 302, and 303 face the space in which the ball screw 20 and structures connected to the ball screw 20 are located.

In this embodiment, the housing 30 has an axial surface (axial wall surface, first axial surface AX1) 311 facing in the first direction and an axial surface (axial wall surface, second axial surface AX2) 312 facing in the second direction. The axial surface 311 is provided between the inner surfaces 302 and 303 in the radial direction and has, for example, a surface perpendicular to the axial direction. The axial surface 312 is provided between the inner surfaces 302 and 301 in the radial direction and has, for example, a surface perpendicular to the axial direction.

The housing 30 is provided with a recess 450 including a space surrounded by the inner surface 302, the axial surface 311, and the axial surface 312. The bearing 40 is disposed in the recess 450. The bearing 40 is inserted into the recess 450 of the housing 30 so that the outer surface 421 of the outer ring 42 faces the inner surface 302 of the housing 30, and the bearing 40 (outer ring 42) and the housing 30 are fitted together. An appropriate interference or gap (loose fit) is provided in the fit between the outer ring 42 and the housing 30. The outer surface (outer peripheral surface) 421 of the bearing 40 (outer ring 42) is supported by the inner surface 302 of the housing 30. The outer ring 42 has an axial surface (axial end surface) 425 facing in the second direction. The axial surface 425 is provided at the end of the outer ring 42 in the second direction and has, for example, a surface perpendicular to the axial direction. The axial surface 425 of the outer ring 42 and the axial surface 311 of the housing 30 face each other and abut against each other. The end face 425 of the outer ring 42 is supported by the axial surface 311 of the housing 30. In FIG. 4, the axial surface 312 of the housing 30 is an axial surface formed integrally with the main body of the housing 30 and faces in the second direction. The axial surface 312 of the housing 30 (second axial surface AX2) and the first surface 501 (third axial surface AX3) of the sliding member 50 are arranged facing each other. The axial surface 312 and the first surface 501 face each other and abut against each other, or face each other with a gap between them.

In this embodiment, during high-load driving, a high load (reaction force, axial load) acts in the second direction (first mode, high-load mode). In the ball screw 20, a high reaction force in the second direction caused by high-load driving acts on the nut 22 via the ball screw 20. In this first mode, the force in the second direction due to the high load is transmitted in the following order: nut 22, sliding member 50, inner ring 41, rolling elements 43, outer ring 42, and housing 30. That is, the axial load from the ball screw 20 is received by the axial surface 311 of the housing 30 via the sliding member 50, inner ring 41, rolling elements 43, and outer ring 42. In the bearing 40, the inner ring 41 rotates relative to the outer ring 42 while bearing a radial load and an axial load. In this ball screw device 11, even when a high axial load acts, the rotational motion of the second assembly 70 (e.g., nut 22) relative to the first assembly 60 (e.g., housing 30) is stably supported. The ball screw device 11 of this embodiment is suitable for high-load applications and is advantageous for compactness.

In the first mode, the sliding member 50 and inner ring 41 are subjected to a strong force in the second direction based on the axial load (reaction force). This force acts in a direction that causes the first surface 501 of the sliding member 50 to move axially away from the axial surface 312 of the housing 30. In one example, the ball screw device 11 is designed so that a substantial gap 900 is created between the axial surface 312 of the housing 30 and the first surface 501 of the sliding member 50 when a high load is applied in the second direction. The design value of the gap 900 in the first mode (high load mode) is defined as the "allowable axial clearance (C1)." In another example, the ball screw device 11 is designed so that the gap 900 (allowable axial clearance C1) between the axial surface 312 of the housing 30 and the first surface 501 of the sliding member 50 is substantially zero when a high load is applied in the second direction.

As the second assembly 70 rotates relative to the first assembly 60, relative movement (relative rotation) occurs in the circumferential direction between the axial surface 312 of the housing 30 and the first surface 501 of the sliding member 50. In the ball screw device 11, when the allowable axial clearance C1 is set to be greater than zero, rotational load (frictional load) due to contact between the housing 30 and the sliding member 50 in the first mode is avoided.

In the ball screw device 11, when the load in the second direction received from the ball screw 20 is relatively small or substantially zero (no load), relative axial movement tends to occur between the inner ring 41 and the outer ring 42 (second mode, low-load mode). As described above, in the first mode, a substantial gap 900 can occur between the axial surface 312 of the housing 30 and the first surface 501 of the sliding member 50. Furthermore, in a low-load or no-load state, such as when the ball screw 20 is operated in an initial state or in a predetermined orientation, a substantial gap 900 can occur. When a substantial gap 900 exists, there is a possibility that the inner ring 41 will attempt to move in a direction away from the outer ring 42 (first direction). This is due, for example, to the fact that the bearing 40 has a structure that makes it easy to separate in the axial direction and/or that an axial component force is generated in the bearing 40 when a radial load is applied.

In this embodiment, the relative axial movement of the inner ring 41 in the first direction is restricted based on the axial positional relationship between the axial surface 312 (second axial surface AX2) of the housing 30 and the first surface 501 (third axial surface AX3) of the sliding member 50. In other words, the relative axial movement of the inner ring 41 is restricted to within the range of the design value (allowable axial clearance C1) of the gap 900 between the axial surface 312 (second axial surface AX2) and the first surface 501 (third axial surface AX3).

In this embodiment, contact between the axial surface 312 of the housing 30 and the first surface 501 of the sliding member 50 is permitted. Based on contact between the axial surface 312 and the first surface 501, relative axial movement of the inner ring 41 in the first direction is limited. The range of the area (sliding area, contact area, opposing area) 910 where the axial surface 312 and the first surface 501 can contact each other is appropriately set in advance. In one example, the radial range of the sliding area 910 is set to include a position (area 910A) radially inward from the outer surface (outer peripheral surface) 412 of the inner ring 41. In other words, contact between the housing 30 and the sliding member 50 is permitted at a position radially inward from the outer surface 412 of the inner ring 41. In other examples, the radial range of the sliding area 910 may be set to a range different from the above. Appropriate setting of the sliding area 910 contributes to stable operation of the bearing 40 and is advantageous for reducing rotational load and extending the life of the bearing 40.

In this embodiment, slippage is permitted between the axial surface 312 of the housing 30 and the first surface 501 of the sliding member 50. In the ball screw device 11, when the first surface 501 abuts against the axial surface 312 during rotation, relative circumferential movement (circumferential slippage) occurs between the axial surface 312 and the first surface 501 accompanied by contact. In other words, slippage (contact slippage) occurs in at least a portion of the slip region 910. In the ball screw device 11, the configuration that permits contact slippage restricts relative axial movement of the inner ring 41 in the first direction even during rotation.

In this embodiment, a configuration can be adopted in which the state of slippage changes depending on the magnitude of the load in the second direction from the ball screw 20. In one example in which the allowable axial clearance C1 is designed to be greater than zero, contact slippage does not occur between the axial surface 312 and the first surface 501 in the first mode (high load mode). This is because the high axial load from the ball screw 20 pushes the inner ring 41 in the second direction, and the presence of the gap 900 prevents the first surface from contacting the axial surface 312 (non-contact slippage). On the other hand, in the second mode (low load mode), the axial load in the second direction from the ball screw 20 is relatively small or zero. Therefore, the position of the inner ring 41 relative to the outer ring 42 (axial relative position) tends to move in the first direction. When the first surface 501 abuts against the axial surface 312 during rotation, contact slippage occurs between the axial surface 312 and the first surface 501. In this example, the state of slippage changes between the non-contact state in the first mode and the contact state in the second mode. The rotational load generated in the sliding region 910 is kept relatively small.

In another example, the allowable axial clearance C1 is designed to be substantially zero. In the first mode (high load mode), contact slippage occurs between the axial surface 312 and the first surface 501. For example, a rotational load (frictional load) based on preload occurs in the slip region 910. In the second mode (low load mode), contact slippage also occurs between the axial surface 312 and the first surface 501. In this example, the rotational load in the slip region 910 may change between the first mode and the second mode. In this example, the change in the relative axial position of the inner ring 41 and the outer ring 42 between the first mode and the second mode is small, and the posture of the bearing 40 is kept relatively constant.

In this embodiment, contact sliding occurs between the first surface 501 of the sliding member 50 and the shaft surface 312 of the housing 30. Because the member that contacts the housing 30 is a separate member from the inner ring 41, there is a high degree of freedom in designing the sliding member 50 in terms of material, surface precision, surface roughness, surface shape, etc. Appropriate design of the sliding structure can reduce wear, improve assembly ease, and improve positioning accuracy, which is advantageous for extending the life of the device.

As described above, this embodiment achieves high reliability and a long lifespan while maintaining a compact configuration and high load specifications, based on a configuration that restricts relative axial movement of the bearing 40.

Second Embodiment
5 is a schematic partial cross-sectional view showing a ball screw device 12 according to a second embodiment. In the following description of the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and their description will be omitted or simplified. Unlike the first embodiment, this embodiment does not include a sliding member between the housing 30 and the inner ring 41. Furthermore, in this embodiment, the first assembly (outer assembly, support) 60 includes the housing 30, the outer ring 42, etc. The second assembly (inner assembly, rotating body) 70 includes the nut 22, the inner ring 41, etc.

In this embodiment, the axial end surface 415 of the inner ring 41 is designed to directly abut the axial surface 225 of the nut 22. The axial surface 312 (second axial surface AX2) of the housing 30 and the axial end surface 415 (third axial surface AX3) of the inner ring 41 are arranged to face each other. The axial end surface 415 is an axial surface formed integrally with the main body of the inner ring 41 and faces in the first direction. The axial surface 312 of the housing 30 is an axial surface formed integrally with the main body of the housing 30 and faces in the second direction. The axial end surface 415 and the axial surface 312 face each other and abut each other, or face each other with a gap between them.

In this embodiment, during high-load driving, a force in the second direction due to the high load is transmitted in the following order: nut 22, inner ring 41, rolling elements 43, outer ring 42, and housing 30 (first mode, high-load mode). That is, the axial load from the ball screw 20 is received by the axial surface 311 of the housing 30 via the inner ring 41, rolling elements 43, and outer ring 42. In the bearing 40, the inner ring 41 rotates relative to the outer ring 42 while bearing radial and axial loads. In the ball screw device 12, even when a high axial load is applied, the rotational motion of the second assembly 70 (e.g., nut 22) relative to the first assembly 60 (e.g., housing 30) is stably supported. The ball screw device 12 of this embodiment is suitable for high-load applications and is advantageous for compactness.

In the first mode, the inner ring 41 is subjected to a strong force in the second direction based on the axial load (reaction force). This force acts in a direction that causes the axial end surface 415 of the inner ring 41 to move axially away from the axial surface 312 of the housing 30. In one example, the ball screw device 12 is designed so that, when subjected to a high load in the second direction, a substantial gap 900 is created between the axial surface 312 of the housing 30 and the axial end surface 415 of the inner ring 41. In other words, the allowable axial clearance C1 is set to be greater than zero. In another example, the ball screw device 12 is designed so that, when subjected to a high load in the second direction, the gap 900 (allowable axial clearance C1) between the axial surface 312 of the housing 30 and the axial end surface 415 of the inner ring 41 is substantially zero.

As the second assembly 70 rotates relative to the first assembly 60, relative movement (relative rotation) occurs in the circumferential direction between the axial surface 312 of the housing 30 and the axial end surface 415 of the inner ring 41. In the ball screw device 12, when the allowable axial clearance C1 is set to be greater than zero, rotational load (frictional load) due to contact between the housing 30 and the inner ring 41 in the first mode is avoided.

In this embodiment, relative axial movement of the inner ring 41 in the first direction is restricted based on the axial positional relationship between the axial surface 312 (second axial surface AX2) of the housing 30 and the axial end surface 415 (third axial surface AX3) of the inner ring 41. That is, the relative axial movement of the inner ring 41 is restricted within the range of the design value (allowable axial clearance C1) of the gap 900 between the axial surface 312 and the axial end surface 415. The axial relative movement of the inner ring 41 in the first direction is restricted based on the axial surface 312 contacting the axial end surface 415 in the sliding region 910. Furthermore, in this embodiment, sliding is permitted between the axial surface 312 of the housing 30 and the axial end surface 415 of the inner ring 41. In the ball screw device 12, the configuration that allows contact sliding restricts relative axial movement of the inner ring 41 in the first direction even during rotation.

In this embodiment, contact slippage occurs between the shaft end surface 415 of the inner ring 41 and the shaft surface 312 of the housing 30. Compared to the first embodiment, the ball screw device 12 has a reduced number of parts, which is advantageous in terms of reducing costs.

(Third embodiment)
FIG. 6 is a schematic partial cross-sectional view showing a ball screw device 13 according to the third embodiment. In the following description of the third embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and their description will be omitted or simplified. In this embodiment, unlike the first embodiment, the housing 30 includes a sliding member 53. The sliding member 53 is provided as a separate member from the main body of the housing 30 (housing main body 330). In this embodiment, the first assembly (outer assembly, support) 60 includes the housing 30, the outer ring 42, etc. The housing 30 includes the housing main body 330 and the sliding member 53. The second assembly 70 (inner assembly, rotating body) includes the nut 22, the inner ring 41, etc.

In this embodiment, the sliding member 53 has a ring shape and includes a first surface 531 facing a first direction and a second surface 532 facing a second direction. The sliding member 53 is fixed to the housing main body 330 with the first surface 531 facing and abutting the axial surface 312 of the housing 30. In FIG. 6, the second surface 532 (second axial surface AX2) of the sliding member 53 and the axial end surface 415 (third axial surface AX3) of the inner ring 41 are arranged facing each other. The second surface 532 and the axial end surface 415 face each other and abut each other, or face each other across a gap. Additionally and/or alternatively, various structures can be applied, including a separate member (not shown) for fixing the sliding member 53 to the housing main body 330 (such as a thrust collar, a C-shaped retaining ring, or annular plate). In one example, the sliding member 53 is a member having a configuration similar to that of a so-called sliding bearing. In another example, a member having a relatively simple spacer-like configuration is used as the sliding member 53.

In this embodiment, as in the second embodiment, during high-load driving, the force in the second direction due to the high load is transmitted in the following order: nut 22, inner ring 41, rolling element 43, outer ring 42, and housing 30 (first mode, high-load mode). In the ball screw device 13, even when a high axial load is applied, the rotational motion of the second assembly 70 (nut 22, etc.) relative to the first assembly 60 (housing 30, etc.) is stably supported.

In the first mode, the inner ring 41 is subjected to a strong force in the second direction based on the axial load (reaction force). This force acts in a direction that causes the axial end surface 415 of the inner ring 41 to move axially away from the axial surface 312 of the housing 30 (the second surface 532 of the sliding member 53). In one example, the ball screw device 13 is designed so that, when a high load is applied in the second direction, a substantial gap 900 is created between the second surface 532 of the sliding member 53 and the axial end surface 415 of the inner ring 41. In other words, the allowable axial clearance C1 is set to be greater than zero. In another example, the ball screw device 13 is designed so that, when a high load is applied in the second direction, the gap 900 (allowable axial clearance C1) between the second surface 532 of the sliding member 53 and the axial end surface 415 of the inner ring 41 is substantially zero.

As the second assembly 70 rotates relative to the first assembly 60, relative movement (relative rotation) occurs in the circumferential direction between the second surface 532 of the sliding member 53 and the axial end surface 415 of the inner ring 41. In the ball screw device 13, when the allowable axial clearance C1 is set to be greater than zero, rotational load (frictional load) due to contact between the sliding member 53 and the inner ring 41 in the first mode is avoided.

In this embodiment, the relative axial movement of the inner ring 41 in the first direction is restricted based on the axial positional relationship between the second surface 532 (second axial surface AX2) of the sliding member 53 and the axial end surface 415 (third axial surface AX3) of the inner ring 41. That is, the relative axial movement of the inner ring 41 is restricted within the range of the design value (allowable axial clearance C1) of the gap 900 between the second surface 532 and the axial end surface 415. The axial end surface 415 of the inner ring 41 contacts the sliding member 53 in the sliding region 910, thereby restricting the relative axial movement of the inner ring 41 in the first direction. Furthermore, in this embodiment, slippage is permitted between the second surface 532 of the sliding member 53 and the axial end surface 415 of the inner ring 41. In the ball screw device 13, the configuration that allows contact slippage restricts the relative axial movement of the inner ring 41 in the first direction even during rotation.

In this embodiment, contact sliding occurs between the second surface 532 of the sliding member 53 and the axial end surface 415 of the inner ring 41. Because the member that contacts the inner ring 41 is a separate member from the housing main body 330, appropriate design of the sliding structure can reduce wear, improve assembly, and improve positioning accuracy. This is advantageous for extending the life of the device.

Alternatively, various shapes are applicable to the sliding member 53. In the modified example shown in FIG. 7, the sliding member 53 has a diameter portion 581 extending radially and a circumferential portion 582 extending from the diameter portion 581 in the second direction. The outer peripheral surface of the sliding member 53 has a diameter corresponding to the inner surface 302 of the housing 30. The sliding member 53 is inserted into the recess 450 of the housing 30 so that the outer peripheral surface of the sliding member 53 faces the inner surface 302 of the housing 30, and the sliding member 53 and the housing 30 are fitted together. An appropriate interference or gap (loose fit) is provided in the fit between the sliding member 53 and the housing 30. The sliding member 53 and the outer ring 42 are arranged side by side in the axial direction. The sliding member 53 is arranged between the axial surface 312 of the housing 30 and the axial surface 424 of the outer ring 42. An axial end surface (first surface 531) of the sliding member 53 facing in the first direction can abut against the axial surface 312 of the housing 30. An axial end surface (axial end surface 585 of the circumferential portion 582) of the sliding member 53 facing in the second direction can abut against the axial surface 424 of the outer ring 42. In one example, the sliding member 53 is sandwiched between the axial surface 312 and the axial end surface 424 with a preload. In another example, the sliding member 53 is disposed between the axial surface 312 and the axial surface 424 with substantially no preload. A second surface 532 facing in the second direction is disposed in the sliding member 53 between the first surface 531 and the axial end surface 585 in the axial direction. The second surface 532 is disposed radially inward from the axial end surface 585 and has, for example, a surface perpendicular to the axial direction. At least a portion of the second surface 532 is disposed facing the axial surface 415 of the inner ring 41. At least a portion of the second surface 532 and the shaft surface 415 face and abut each other, or face each other across a gap. In the example of Figure 7, the shaft surface 415 of the inner ring 41 contacts the second surface 532 of the sliding member 53, thereby restricting relative axial movement of the inner ring 41 in the first direction.

(Fourth embodiment)
FIG. 8 is a schematic partial cross-sectional view showing a ball screw device 14 according to a fourth embodiment. In the following description of the fourth embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and their description will be omitted or simplified. In this embodiment, unlike the first embodiment, the ball screw 20 includes a sliding member 54. The sliding member 54 is provided as a separate member from the main body of the screw shaft 21/nut 22. In this embodiment, the first assembly (outer assembly, support) 60 includes the housing 30, the outer ring 42, etc. The second assembly 70 (inner assembly, rotating body) includes the nut 22, the inner ring 41, the sliding member 54, etc.

In this embodiment, the housing 30 has an axial surface 315 facing the second direction. The nut 22 has an axial surface 226 facing the first direction. The axial surface 315 and the axial surface 226 are arranged opposite each other. The sliding member 54 is arranged between the axial surface 315 and the axial surface 226. The sliding member 54 is ring-shaped and has a first surface 541 facing the first direction and a second surface 542 facing the second direction. The sliding member 54 is fixed to the nut 22 while facing and abutting against the nut 22. The axial surface 315 (second axial surface AX2) of the housing 30 and the first surface 541 (third axial surface AX3) of the sliding member 54 are arranged facing each other. The axial surface 315 and the first surface 541 face each other and abut each other, or face each other with a gap between them. Additionally and/or alternatively, various structures can be applied that include a separate member (not shown) for securing the sliding member 54 to the nut 22 (such as a thrust collar, a C-shaped retaining ring, or annular plate). In one example, a member having a configuration similar to that of a sliding bearing is used as the sliding member 54. In another example, a member having a configuration similar to that of a relatively simple spacer is used as the sliding member 54.

In this embodiment, as in the second embodiment, during high-load driving, a force in the second direction due to the high load is transmitted in the following order: nut 22, inner ring 41, rolling element 43, outer ring 42, and housing 30 (first mode, high-load mode). In the ball screw device 14, even when a high axial load is applied, the rotational motion of the second assembly 70 (nut 22, etc.) relative to the first assembly 60 (housing 30, etc.) is stably supported.

In the first mode, the nut 22 is subjected to a strong force in the second direction based on the axial load (reaction force). This force acts in a direction that causes the axial surface 226 of the nut 22 (the first surface 541 of the sliding member 54) to move axially away from the axial surface 315 of the housing 30. In one example, the ball screw device 14 is designed so that, when a high load is applied in the second direction, a substantial gap 900 is created between the axial surface 315 of the housing 30 and the first surface 541 of the sliding member 54. In other words, the allowable axial clearance C1 is set to be greater than zero. In another example, the ball screw device 14 is designed so that, when a high load is applied in the second direction, the gap 900 (the allowable axial clearance C1) between the axial surface 315 of the housing 30 and the first surface 541 of the sliding member 54 is substantially zero.

As the second assembly 70 rotates relative to the first assembly 60, relative movement (relative rotation) occurs in the circumferential direction between the axial surface 315 of the housing 30 and the first surface 541 of the sliding member 54. In the ball screw device 14, when the allowable axial clearance C1 is set to be greater than zero, rotational load (frictional load) due to contact between the housing 30 and the sliding member 54 in the first mode is avoided.

In this embodiment, the relative axial movement of the inner ring 41 in the first direction is restricted based on the axial positional relationship between the axial surface 315 (second axial surface AX2) of the housing 30 and the first surface 541 (third axial surface AX3) of the sliding member 54. That is, the relative axial movement of the inner ring 41 is restricted within the range of the design value (allowable axial clearance C1) of the gap 900 between the axial surface 315 and the first surface 541. The first surface 541 of the sliding member 54 contacts the axial surface 315 of the housing 30 in the sliding region 910, thereby restricting the relative axial movement of the inner ring 41 in the first direction. Furthermore, in this embodiment, slippage is permitted between the axial surface 315 of the housing 30 and the first surface 541 of the sliding member 54. In the ball screw device 14, the configuration that allows contact slippage restricts the relative axial movement of the inner ring 41 in the first direction even during rotation.

In this embodiment, contact sliding occurs between the shaft surface 315 of the housing 30 and the first surface 541 of the sliding member 54. Because the member that comes into contact with the housing 30 is a separate member from the nut 22, appropriate design of the sliding structure can reduce wear, improve assembly ease, and improve positioning accuracy. This is advantageous for extending the life of the device.

In addition, in this embodiment, the radial range of the sliding region 910 is set to include a position (region 910A) radially inward relative to the outer surface (outer peripheral surface) 412 of the inner ring 41, and a position (region 910B) radially inward relative to the rolling elements 43. In other words, contact between the housing 30 and the sliding member 54 is permitted at a position radially inward relative to the rolling elements 43. Appropriate setting of the sliding region 910 contributes to stable operation of the bearing 40 and is advantageous for reducing rotational load and extending the life of the bearing 40.

In the example shown in FIG. 8, the radial range of the sliding area 910 is set at a position radially inward relative to the rolling elements 43. Alternatively, at least a portion of the radial range of the sliding area 910 may be set at a position radially outward relative to the rolling elements 43. Also, at least a portion of the radial range of the sliding area 910 may be set at a position radially outward relative to the outer surface (outer peripheral surface) 412 of the inner ring 41.

8, the ball screw 20 is provided with a sliding member 54. In a modified example of FIG. 8, a configuration in which a sliding member is provided on the housing 30 at a position axially spaced from the bearing 40 can be applied. That is, a sliding member fixed to the housing 30 may be disposed between the axial surface of the housing 30 and the axial surface of the ball screw 20. In this example, the relative axial movement of the nut 22 and the inner ring 41 in the first direction is restricted based on the axial positional relationship between the axial surface (second axial surface AX2) of the sliding member provided on the housing 30 and the axial surface (third axial surface AX3) of the nut 22. Furthermore, in another modified example, the sliding structure may be configured without a sliding member, as in the second embodiment. In this configuration, the axial surface of the nut 22 and the axial surface of the housing 30 directly face each other at a position axially spaced from the bearing 40, and contact sliding occurs between the axial surface of the nut 22 and the axial surface of the housing 30.

(Fifth, Sixth, and Seventh Embodiments)
9A and 9B are schematic cross-sectional views showing ball screw devices 15, 16, and 17 according to fifth, sixth, and seventh embodiments. FIG. 9A shows the ball screw device 15 according to a fifth embodiment, which is a modification of the first embodiment. FIG. 9B shows the ball screw device 16 according to a sixth embodiment, which is a modification of the second embodiment. FIG. 9C shows the ball screw device 17 according to a seventh embodiment, which is a modification of the third embodiment. In the following description, the same components as those in the above embodiments are denoted by the same reference numerals, and their description will be omitted or simplified. In each embodiment, the ball screw devices 15, 16, and 17 further include a preload member 80.

In the fifth embodiment shown in FIG. 9(a), the ball screw device 15 is configured so that the axial surface 312 (second axial surface AX2) of the housing 30 and the first surface 501 (third axial surface AX3) of the sliding member 50 approach each other due to the preload of the preload member 80. In one example, the preload member 80 is an elastic member, such as a disc spring. For example, the preload member 80 is disposed between the axial end surface 425 of the outer ring 42 and the axial surface 311 of the housing 30 in a pre-elastically deformed state. The preload member 80 applies a biasing force (preload) to the outer ring 42 in a first direction based on its elastic deformation. Furthermore, the shape (elastically deformed state) of the preload member 80 changes in response to a load acting on the bearing 40 in a second direction. In other examples, a preload mechanism other than those described above is used.

In this embodiment, in both the high load state (first mode) and the low load state (second mode), the preload from the preload member 80 acts on the bearing 40. Furthermore, in the second mode, the preload from the preload member 80 causes the axial surface 312 (second axial surface AX2) of the housing 30 and the first surface 501 (third axial surface AX3) of the sliding member 50 to come into contact with each other. This is also true for the sixth embodiment shown in FIG. 9(b) and the seventh embodiment shown in FIG. 9(c). Similarly, a configuration further including a preload member 80 can also be applied to the fourth embodiment.

In the fifth, sixth, and seventh embodiments, the preload applied by the preload member 80 suppresses axial movement of the bearing 40 relative to the gap 900. As a result, problems such as damage to the bearing 40 and abnormal noise are reliably prevented, for example, by reducing noise and vibration.

(Eighth, Ninth, and Tenth Embodiments)
10 and 11 are schematic cross-sectional views showing ball screw devices 81, 82, and 83 according to eighth, ninth, and tenth embodiments. FIGS. 10 and 11(a) show a ball screw device 81 according to an eighth embodiment, which is a modified version of the first embodiment. FIG. 11(b) shows a ball screw device 82 according to a ninth embodiment, which is a modified version of the second embodiment. FIG. 11(c) shows a ball screw device 83 according to a tenth embodiment, which is a modified version of the third embodiment. In the following description, the same components as those in the above embodiments are denoted by the same reference numerals, and their description will be omitted or simplified. In each embodiment, the ball screw devices 81, 82, and 83 are configured so that the screw shaft 21 of the ball screw 20 rotates relative to the housing 30.

As shown in Figure 10, in the eighth embodiment, a first shaft 91 to which the driving force of a motor (not shown) is transmitted is connected to a screw shaft 21. The ball screw 20 converts rotational motion into linear motion.

In this embodiment, the inner ring 41 of the bearing 40 is attached to the screw shaft 21 of the ball screw 20, and the outer ring 42 of the bearing 40 is attached to the housing 30. Additionally and/or alternatively, various structures can be applied that include a separate member (not shown) (such as a thrust collar, a C-shaped retaining ring, or annular plate) for supporting the axial position of the inner ring 41 relative to the screw shaft 21.

As shown in FIG. 11(a), the outer diameter of the bearing 40 is larger than the outer diameter of the screw shaft 21. In other examples, the outer diameter of the bearing 40 can be smaller than the outer diameter of the screw shaft 21. In FIG. 11(a), the bearing 40 is positioned substantially radially outward of the screw shaft 21. The screw shaft 21 has outer surfaces 211, 212 facing radially outward. The outer surface (outer circumferential surface) 212 of the screw shaft 21 has an outer diameter corresponding to the diameter of the hole in the bearing 40 (the inner diameter of the inner ring 41). A portion of the screw shaft 21 is inserted into the hole in the bearing 40 so that the outer surface 212 of the screw shaft 21 and the inner surface (inner circumferential surface) 411 of the inner ring 41 face each other, thereby fitting the screw shaft 21 and the bearing 40 (inner ring 41) together. The inner surface 411 of the bearing 40 (inner ring 41) is supported by the outer surface 212 of the screw shaft 21. An appropriate interference or gap (loose fit) is provided when the screw shaft 21 and inner ring 41 are fitted together. In another example, the screw shaft 21 and inner ring 41 can be formed integrally.

In this embodiment, the screw shaft 21 has an axial surface (axial wall surface) 215 facing the second direction. The axial surface 215 is located between the outer surfaces 211 and 212 in the radial direction and has, for example, a surface perpendicular to the axial direction. The axial surface 215 of the screw shaft 21 is positioned opposite the axial end surface 415 of the inner ring 41.

In this embodiment, a sliding member 50 is disposed between the axial surface 215 of the screw shaft 21 and the axial end surface 415 of the inner ring 41. The sliding member 50 is fixed to the screw shaft 21 and the inner ring 41 by being sandwiched between them. In this embodiment, the first assembly (outer assembly, support body) 60 includes the housing 30, the outer ring 42, etc. The second assembly (inner assembly, rotating body) 70 includes the screw shaft 21, the inner ring 41, and the sliding member 50, etc.

In this embodiment, a high reaction force in the second direction caused by driving under a high load acts on the screw shaft 21 via the ball screw 20. In this first mode, the force in the second direction due to the high load is transmitted in the following order: screw shaft 21, sliding member 50, inner ring 41, rolling elements 43, outer ring 42, and housing 30. In the ball screw device 11, even when a high axial load is applied, the rotational motion of the second assembly 70 (e.g., screw shaft 21) relative to the first assembly 60 (e.g., housing 30) is stably supported.

In this embodiment, as in the first embodiment, the relative axial movement of the inner ring 41 in the first direction is restricted based on the axial positional relationship between the axial surface 312 (second axial surface AX2) of the housing 30 and the first surface 501 (third axial surface AX3) of the sliding member 50. That is, the relative axial movement of the inner ring 41 is restricted within the range of the design value (allowable axial clearance C1) of the gap 900 between the axial surface 312 (second axial surface AX2) and the first surface 501 (third axial surface AX3). The first surface 501 of the sliding member 50 contacts the axial surface 312 of the housing 30, thereby restricting the relative axial movement of the inner ring 41 in the first direction. Furthermore, based on contact sliding in the sliding region 910, the relative axial movement of the inner ring 41 in the first direction is restricted even during rotation.

Thus, in this embodiment, even though the screw shaft 21 rotates relative to the housing 30, similar to the first embodiment, high reliability and long life are achieved while maintaining a compact configuration and high load specifications based on a configuration that restricts relative axial movement of the bearing 40. The same is true for the ninth embodiment shown in Figure 11(b) and the tenth embodiment shown in Figure 11(c).

(Eleventh, twelfth, and thirteenth embodiments)
12A and 12B are schematic partial cross-sectional views showing ball screw devices 84, 85, and 86 according to 11th, 12th, and 13th embodiments. FIG. 12A shows a ball screw device 84 according to an 11th embodiment, which is a modification of the eighth embodiment. FIG. 12B shows a ball screw device 85 according to a 12th embodiment, which is a modification of the ninth embodiment. FIG. 12C shows a ball screw device 86 according to a 13th embodiment, which is a modification of the tenth embodiment. In the following description, the same components as those in the above embodiments are denoted by the same reference numerals, and their description will be omitted or simplified. In each embodiment, the ball screw devices 84, 85, and 86 further include a preload member 80.

In the eleventh embodiment shown in FIG. 12(a), the ball screw device 84 is configured so that the axial surface 312 (second axial surface AX2) of the housing 30 and the first surface 501 (third axial surface AX3) of the sliding member 50 approach each other due to the preload of the preload member 80. In this embodiment, the preload of the preload member 80 acts on the bearing 40 in both the high-load state (first mode) and the low-load state (second mode). In the second mode, the preload of the preload member 80 causes the axial surface 312 (second axial surface AX2) of the housing 30 and the first surface 501 (third axial surface AX3) of the sliding member 50 to come into contact with each other. This is also true in the twelfth embodiment shown in FIG. 12(b) and the thirteenth embodiment shown in FIG. 12(c).

In the 11th, 12th, and 13th embodiments, the preload applied by the preload member 80 suppresses axial movement of the bearing 40 relative to the gap 900. As a result, problems such as damage to the bearing 40 and abnormal noise are reliably prevented, for example, by reducing noise and vibration.

The technical scope of the present invention is not limited to the scope described in the embodiments. Various modifications and improvements can be made to the embodiments. Forms incorporating such modifications or improvements can also be included within the technical scope of the present invention. Furthermore, the present invention is not limited to the described embodiments, and any combination of these configurations may be used.

The present disclosure may be combined as follows:
(1) In one embodiment, a ball screw device includes a ball screw having a screw shaft, a nut, and multiple balls; a housing supporting the ball screw; and a bearing having an inner ring, an outer ring, and multiple rolling elements. The bearing is disposed between the ball screw and the housing and has a structure capable of bearing radial loads and axial loads. The housing has a first axial surface facing a first direction and a second axial surface facing a second direction. An axial load from the ball screw along the second direction is received by the first axial surface via the inner ring, the rolling elements, and the outer ring. The bearing or the ball screw has a third axial surface disposed facing the second axial surface. The second axial surface and the third axial surface face each other and abut against each other, or face each other via a gap. When the screw shaft or the nut rotates relative to the housing, relative movement in the circumferential direction occurs between the second axial surface and the third axial surface. Axial relative movement of the inner ring relative to the outer ring in the first direction is restricted based on the axial positional relationship between the second axial surface and the third axial surface.
(2) In the ball screw device described in (1) above, contact between the second shaft surface and the third shaft surface is permitted.
(3) In the ball screw device described in (1) or (2) above, sliding is permitted between the second shaft surface and the third shaft surface.
(4) In the ball screw device described in (3) above, the state of the slippage changes depending on the magnitude of the axial load from the ball screw.
(5) In the ball screw device described in any one of (1) to (4) above, the bearing or the ball screw has an axial surface as the third axial surface formed on the body of the bearing, the screw shaft, or the nut, or is provided with a sliding member having the third axial surface as a separate member from the body of the bearing, the screw shaft, or the nut.
(6) In the ball screw device described in any one of (1) to (4) above, the housing has an axial surface as the second axial surface formed on the main body of the housing, or is provided with a sliding member having the second axial surface as a separate member from the main body of the housing.
(7) The ball screw device according to any one of (1) to (6) above further comprises a preload member that applies a preload so that the second axial surface and the third axial surface approach each other.
(8) In the ball screw device according to any one of (1) to (7) above, the bearing is a single-row tapered roller bearing or a single-row angular contact ball bearing.

11 to 17, 81 to 86 Ball screw device,
20 ball screw,
21 screw shaft,
22 nuts,
30 housing,
40 bearings,
41 Inner circle,
42 outer ring,
43 rolling elements,
50, 53, 54 Sliding member (sliding bearing, regulating member),
60 first assembly,
70 second assembly,
80 Preload member,
900 gap,
AX1 1st axis plane,
AX2 second axis surface,
AX3 Third axis surface.

Claims (11)

a ball screw having a screw shaft, a nut, and a plurality of balls;
a housing that supports the ball screw;
a bearing having an inner ring, an outer ring, and a plurality of rolling elements;
Equipped with
the bearing is disposed between the ball screw and the housing and has a structure capable of bearing a radial load and an axial load,
The housing has a first axial surface oriented in a first direction and a second axial surface oriented in a second direction;
the first direction is opposite to the second direction,
an axial load from the ball screw along the second direction is received by the first axial surface via the inner ring, the rolling elements, and the outer ring;
the bearing or the ball screw has a third axial surface arranged facing the second axial surface,
When the screw shaft or the nut rotates relative to the housing, a relative movement in a circumferential direction occurs between the second axial surface and the third axial surface,
Axial relative movement of the inner ring with respect to the outer ring in the first direction is restricted based on an axial positional relationship between the second axial surface and the third axial surface.
Ball screw device. The ball screw device according to claim 1, wherein contact between the second shaft surface and the third shaft surface is permitted. The ball screw device of claim 1, wherein sliding is permitted between the second axial surface and the third axial surface. The ball screw device described in claim 3, wherein the state of slippage changes depending on the magnitude of the axial load from the ball screw. the outer ring has a fourth axial surface oriented in the first direction and a fifth axial surface oriented in the second direction,
the rolling element is located between the fourth axial surface and the fifth axial surface in the axial direction,
the third axial surface is located between the second axial surface and the fourth axial surface in the axial direction,
A space is provided between the second axial surface and the fourth axial surface.
The ball screw device according to claim 1 . The bearing, the screw shaft, or the nut body further includes a sliding member having the second axial surface as a separate member,
the outer ring has a fourth axial surface oriented in the first direction and a fifth axial surface oriented in the second direction,
the rolling element is located between the fourth axial surface and the fifth axial surface in the axial direction,
the third axial surface is located between the second axial surface and the fourth axial surface in the axial direction,
The sliding member is fixed to the housing.
The ball screw device according to claim 1 . The bearing, the screw shaft, or the nut body further includes a sliding member having the third axial surface as a separate member,
the outer ring has a fourth axial surface oriented in the first direction and a fifth axial surface oriented in the second direction,
the rolling element is located between the fourth axial surface and the fifth axial surface in the axial direction,
the third axial surface is located between the second axial surface and the fourth axial surface in the axial direction,
The sliding member is disposed between the second axial surface and the fourth axial surface.
The ball screw device according to claim 1 . 6. The ball screw device according to claim 1, wherein the bearing or the ball screw has an axial surface as the third axial surface formed on the body of the bearing, the screw shaft, or the nut, or comprises a sliding member having the third axial surface as a separate member from the body of the bearing, the screw shaft, or the nut . 6. A ball screw device according to claim 1, wherein the housing has an axial surface as the second axial surface formed on a main body of the housing, or the housing is provided with a sliding member having the second axial surface as a separate member from the main body of the housing . The ball screw device according to claim 1 , further comprising a preload member that applies a preload so that the second axial surface and the third axial surface approach each other. 8. The ball screw device according to claim 1 , wherein the bearing is a single-row tapered roller bearing or a single-row angular contact ball bearing.