JP2017180688A - Rolling bearing-type transmission mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing-type transmission mechanism capable of reliably and easily realizing a state in which an inner ring body is relatively movable in an axial direction though it is not relatively rotatable around an axis with respect to a rotating shaft.SOLUTION: A rolling bearing-type transmission mechanism includes a ring-shaped inner collar member fitted to an inner ring body in a state in which it is not relatively rotatable around an axis and not relatively movable in an axial direction, and/or a ring-shaped outer collar member externally fitted to an outer ring body in a state in which it is not relatively rotatable around an axis and is not relatively movable in an axial direction. The inner collar member is provided with an engagement structure for making the inner collar member relatively non-rotatable around an axis and relatively movable in an axial direction with respect to a rotating shaft. The outer collar member is provided with an engagement structure for engaging the outer collar member in a state in which it is not rotatable around an axis and is movable in an axial direction with respect to a fixing member.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a rolling bearing type transmission mechanism.

  An outer ring body that cannot rotate around its axis in a state of surrounding the inner ring body so that a gap exists between an inner ring body that is relatively non-rotatable around the axis of rotation and an outer peripheral surface of the inner ring body in the radial direction. And a plurality of rolling elements sandwiched between the inner ring body and the outer ring body, the rolling bearing type transmission mechanism holds the plurality of rolling elements at a predetermined interval in the circumferential direction, and the plurality of rolling elements. Along with the revolution of the moving body, it cooperates with a cage that rotates about the same axis as the inner ring body to transmit power transmission between the rotating shaft and the cage. For example, it is disclosed in Patent Document 1 below. As is known.

  The rolling bearing type transmission mechanism is easy to manufacture by diverting a commercially available rolling bearing that is highly accurate but has a mass production effect and low cost, and uses a cage as a power transmission member. This is useful in that it can be downsized in the radial direction as compared with the transmission mechanism, can prevent power loss due to tooth surface friction, and can prevent noise caused by gear meshing.

  By the way, in order for the rolling bearing transmission mechanism to effectively perform a power transmission function, it is necessary to generate a preload in a predetermined range between the rolling element and the inner ring body and the outer ring body. That is, if the preload is too large, the life is shortened, and if it is too small, the transmission efficiency is deteriorated. Therefore, it is necessary to manage it within an appropriate range.

  Specifically, in the configuration described in Patent Document 1, the inner ring body is provided with an inner angle groove that faces the one side in the axial direction and the outer side in the radial direction on the outer peripheral surface on which the rolling element slides. The outer ring body is provided with an outer angle groove facing the other side in the axial direction and the inner side in the radial direction so as to face the inner angle groove with the rolling element interposed therebetween on the inner peripheral surface with which the rolling element slides.

  The inner ring body is pressed to one side in the axial direction by the preload means in a state in which the inner ring body is supported relative to the rotation shaft so as not to rotate relative to the axis and is relatively movable in the axial direction, and the outer ring body cannot rotate around the axis on the housing. It is installed so that it cannot move to one side in the axial direction.

  With this configuration, the pressing force applied to the inner ring body on the one side in the axial direction by the preload means is transmitted to the outer ring body as the force for pressing the outer ring body on the one side in the axial direction via the rolling elements. As a result, a preload is generated between the rolling elements and the inner and outer ring bodies.

  Here, in order to generate the preload by pressing one of the inner ring body having the inner angle groove and the outer ring body having the outer angle groove along the axial direction by the preload means, the inner ring body and the outer ring body Among them, at least the ring body pressed by the preload means (in the configuration described in Patent Document 1, the inner ring body) needs to be movable in the axial direction.

In other words, in the configuration in which the inner ring body is pressed in the axial direction by the preload means as described in Patent Document 1, the inner ring body that is not relatively rotatable about the axis with respect to the rotating shaft is It is necessary to support the shaft so that it can move relative to the axis of rotation.
However, Patent Document 1 does not fully consider how to realize such a state.

  Further, in the configuration in which the outer ring body is pressed in the axial direction by the preload means, the outer ring body that is installed in the housing so as not to rotate about the axis needs to be movable with respect to the housing in the axial direction. .

JP 2014-152800 A

The present invention has been made in view of the above-described prior art, and it is possible to reliably and easily realize a state in which the inner ring body is relatively non-rotatable around the axis while being relatively movable in the axial direction. The first object is to provide a bearing type transmission mechanism.
The present invention also provides a rolling bearing type transmission mechanism that can reliably and easily realize a state in which the outer ring body is movable in the axial direction while being unable to rotate around the axis with respect to a fixing member such as a housing. The purpose of 2.

  In order to achieve the first object, the present invention surrounds the inner ring body such that there is a gap between the inner ring body that is relatively unrotatable about the axis about the rotation shaft and the inner ring body in the radial direction. An outer ring body and a plurality of rolling elements sandwiched between the inner ring body and the outer ring body, and an outer peripheral surface of the inner ring body and an inner peripheral surface of the outer ring body that are in sliding contact with the rolling elements, A rolling bearing type transmission mechanism provided with an inner angle groove and an outer angle groove facing each other with the rolling element interposed therebetween, and is fitted into the inner ring body so as not to be relatively rotatable about an axis and not relatively movable in the axial direction. A ring-shaped inner collar member, and the inner collar member is configured to be extrapolated and supported by the rotating shaft, and the inner collar member is supported in an extrapolated manner by the rotating shaft. Inner collar The engagement structure for the axis about relative rotation and axially movable relative to providing a rolling bearing type transmission mechanism is provided for the rotary shaft.

Preferably, the rolling bearing type transmission mechanism according to the present invention may include a ring-shaped outer collar member that is externally fitted to the outer ring body so as not to be relatively rotatable about the axis and not to be relatively movable in the axial direction.
The outer collar member is configured to be inserted into a non-rotatable fixing member, and the outer collar member is inserted into the fixing member in a state where the outer collar member is inserted into the fixing member. An engagement structure is provided that engages with each other so as not to rotate around the axis and to be movable in the axial direction.

  Further, in order to achieve the second object, the present invention provides the inner ring body such that a gap exists between the inner ring body that is relatively unrotatable about the axis about the rotation shaft and the inner ring body in the radial direction. An outer ring body surrounding the inner ring body, and a plurality of rolling elements sandwiched between the inner ring body and the outer ring body, and an outer peripheral surface of the inner ring body and an inner peripheral surface of the outer ring body that are in sliding contact with the rolling elements, Each of the rolling bearing transmission mechanisms is provided with an inner angle groove and an outer angle groove facing each other across the rolling element, and the outer ring body cannot be relatively rotated around the axis and cannot be relatively moved in the axial direction. The outer collar member includes a ring-shaped outer collar member that is externally fitted, and the outer collar member is configured to be inserted into a non-rotatable fixing member. The outer collar member is inserted into the fixing member. In the installed state Providing rolling bearing type transmission mechanism engaging structure for engaging about an axis non-rotatable and axially movably engaged with respect to the fixed member the outer collar member.

In the various configurations, the engagement structure is preferably a spline structure.
Instead, a groove along the axial direction is formed on the opposing surfaces of the outer collar member and the fixing member so as to face each other, and the engagement structure is a groove of the outer collar member and the fixing member. It is possible to include an engagement hole defined by the above-described configuration and a pin inserted through the engagement hole.

According to the rolling bearing type transmission mechanism according to the first aspect of the present invention, a ring-shaped inner collar member fitted into the inner ring body so as not to be relatively rotatable about the axis and to be relatively unmovable in the axial direction is provided. The inner collar member is configured to be extrapolated and supported by the rotating shaft, and the inner collar member cannot be relatively rotated around the axis with respect to the rotating shaft while being extrapolated and supported by the rotating shaft. An engagement structure that allows relative movement in the axial direction is provided, so that the inner ring body can be relatively moved in the axial direction while being relatively unrotatable about the rotational axis. Thus, it is possible to appropriately apply a preload to the inner ring body, and to improve the transmission efficiency of the rolling bearing type transmission mechanism.
Further, by forming the inner collar member so as to fill a gap generated between the rotating shaft and the inner ring body, the inner ring body and the outer ring body are not special and are mass-produced and generally marketed. It becomes possible to use the inner ring body and the outer ring body of the angular ball bearing as they are.

The rolling bearing transmission mechanism according to the second aspect of the present invention further includes a ring-shaped outer collar member that is externally fitted to the outer ring body so as not to be relatively rotatable about the axis and to be relatively unmovable in the axial direction. The collar member is configured to be inserted into a non-rotatable fixing member, and the outer collar member is inserted into the fixing member with respect to the fixing member. Since the engagement structure is provided so as to be non-rotatable around the axis and movable in the axial direction, the outer ring body can be relatively moved in the axial direction while being relatively unrotatable around the axis with respect to the fixed member. The state can be realized reliably and easily, the preload load can be appropriately applied to the outer ring body, and the transmission efficiency of the rolling bearing type transmission mechanism can be improved.
Further, by forming the outer collar member so as to fill a gap generated between the fixing member and the outer ring body, the inner ring body and the outer ring body are not special and are mass-produced and generally marketed. It becomes possible to use the inner ring body and the outer ring body of the angular ball bearing as they are.

FIG. 1 is a cross-sectional view of a hydraulic continuously variable transmission to which a drive mechanism including a rolling bearing transmission mechanism according to Embodiment 1 of the present invention is applied as a speed increasing transmission. FIG. 2 is a sectional view of the drive mechanism including the rolling bearing type transmission mechanism according to the first embodiment. FIG. 3 is a perspective view of a cage in the drive mechanism. FIG. 4 is a sectional view of a drive mechanism including a rolling bearing transmission mechanism according to Embodiment 2 of the present invention. FIG. 5 is a cross-sectional view of a drive mechanism including a rolling bearing type transmission mechanism according to Embodiment 3 of the present invention. FIG. 6 is a cross-sectional view taken along the line VI-VI in FIG.

Embodiment 1
Hereinafter, an embodiment of a rolling bearing transmission mechanism according to the present invention will be described with reference to the accompanying drawings.
FIG. 1 is a sectional view of a hydraulic continuously variable transmission (HST) 1 to which a drive mechanism 100A including a rolling bearing transmission mechanism 145A according to the present embodiment is applied.
FIG. 2 is a sectional view of the drive mechanism 100A.

First, the HST1 will be described.
As shown in FIG. 1, the HST 1 is supported by the HST case 10, the pump shaft 20 and the motor shaft 40 that are rotatably supported by the HST case 10, and the pump shaft 20 so as not to be relatively rotatable. A hydraulic pump 30 housed in the HST case 10 in a state and a hydraulic motor 50 housed in the HST case 10 in a state supported relative to the motor shaft 40 so as not to rotate relative to each other are provided.

The pump shaft 20 forms an input end whose first end 21 is operatively connected to a drive source (not shown).
In the present embodiment, as shown in FIG. 1, both the first end 21 forming the input end and the second end 22 opposite to the first end 21 are formed in the HST case 10. The HST case 10 is supported by the HST case 10 so as to be rotatable about the axis while being extended outwardly.

  The second end 22 of the pump shaft 20 acts as an output end that outputs rotational power to a drive member such as a charge pump that is to be driven by rotational power from the drive source.

The motor shaft 40 functions as an output shaft of the HST1.
The motor shaft 40 is supported by the HST case 10 so as to be rotatable about an axis line with an end portion forming an output end portion extending outward from the HST case 10.

  In the present embodiment, as shown in FIG. 1, the motor shaft 40 is arranged in parallel with the pump shaft 20, and is on the same side of the motor shaft 40 as the second end 22 of the pump shaft 20. Is extended outward from the HST case 10 to serve as an output end.

The hydraulic pump 30 and the hydraulic motor 50 are fluidly connected to each other, and at least one of the volumes is variable.
Specifically, the HST 1 has a pump swash plate 35 and a motor swash plate 55 that define the capacities of the hydraulic pump 30 and the hydraulic motor 50, respectively.
As shown in FIG. 1, in this embodiment, the pump swash plate 35 is a movable swash plate, and the motor swash plate 55 is a fixed swash plate.

A pair of hydraulic fluid passages (not shown) that fluidly connect the hydraulic pump 30 and the hydraulic motor 50 are formed in the HST case 10.
Specifically, the HST case 10 includes an HST case main body 11 having an opening 11a on one side in the rotational axis direction, and a port block 15 removably connected to the HST case 11 so as to close the opening 11a. doing.

The hydraulic pump 30 and the hydraulic motor 50 are accommodated in an HST accommodating space 10 a defined by the HST case main body 11 and the port block 15 in a slidable contact state with the inner surface of the port block 15.
In such a configuration, the pair of hydraulic oil passages are formed in the pair of port blocks 15.

  The drive mechanism 100A is attached to the HST 1 so as to act as a speed increasing transmission device that accelerates the rotational power from the drive source and transmits it to the pump shaft 20.

  As shown in FIGS. 1 and 2, the drive mechanism 100A includes the transmission mechanism 145A including an inner collar member 120, which will be described later, a retainer 170, and a preload means 200 according to the present embodiment. Yes.

  The transmission mechanism 145A has a gap between the inner ring body 115 connected to the corresponding rotating shaft (the pump shaft 20 in the present embodiment) so as not to rotate relative to the axis, and the inner ring body 115 in the radial direction. As shown, the outer ring body 135 surrounding the inner ring body 115 and the plurality of rolling elements 150 sandwiched between the inner ring body 115 and the outer ring body 135 are provided.

  On the outer peripheral surface of the inner ring body 115 and the inner peripheral surface of the outer ring body 135 with which the rolling element 150 is in sliding contact, an inner angle groove 116 and an outer angle groove 136 that face each other with the rolling element 150 interposed therebetween, respectively. Is provided.

  As shown in FIG. 2, in the drive mechanism 100A, the two rolling bearing type transmission mechanisms 145A diverting rolling bearings extend along the axial direction of the rotating shaft (the pump shaft 20 in the present embodiment). Are arranged in series.

  Of the two transmission mechanisms 145A, the transmission mechanism 145A (hereinafter referred to as the first transmission mechanism 145A (1) as appropriate) arranged on one side in the axial direction has the inner angle groove 116 on one side in the axial direction. In addition, the outer angle groove 136 is disposed in a posture facing the radially outer side and facing the other axial side and the radially inner side.

  On the other hand, of the two transmission mechanisms 145A, the transmission mechanism 145A (hereinafter, appropriately referred to as the second transmission mechanism 145A (2)) arranged on the other side in the axial direction replaces the first transmission mechanism 145A (1). In a posture reversed in the axial direction, that is, the inner angle groove 116 faces the other axial direction and the radially outer side, and the outer angle groove 136 faces the one axial direction and the radially inner side. ing.

  In the following description, the inner ring body 115, the rolling element 150, and the outer ring body 135 of the first transmission mechanism 145A (1) are appropriately connected to the first inner ring body 115 (1) and the first rolling element 150, respectively. (1) and the first outer ring body 135 (1), the inner ring body 115, the rolling element 150 and the outer ring body 135 of the second transmission mechanism 145A (2) are respectively referred to as the second inner ring body 115 (2 ), The second rolling element 150 (2) and the second outer ring body 135 (2).

  The cage 170 holds the plurality of rolling elements 150 at a predetermined interval in the circumferential direction, and rotates the transmission around the same axis as the inner ring body 115 as the plurality of rolling elements 150 revolve. It is assembled to the mechanism 145A.

  As shown in FIG. 2, in the present embodiment, the cage 170 corresponds to the inner ring body 115 corresponding to the first rolling element 150 (1) and the second rolling element 150 (2) in a synchronized state. (1), the first rolling element 150 (1) and the second rolling element 150 (2) are held so as to revolve around 115 (2) and the first rolling element 150 (1). And it is comprised so that it may rotate around an axis line with the synchronous revolution operation | movement of the said 2nd rolling element 50 (2).

FIG. 3 shows a perspective view of the cage 170.
Specifically, as shown in FIG. 3, the cage 170 corresponds to the first and second inner ring bodies corresponding to the first rolling element 150 (1) and the second rolling element 150 (2) in a synchronized state. 115 (1), 115 (2) so as to revolve around the first rolling element 150 (1) and the second rolling element 150 (2) in a circumferential direction at a predetermined interval. A connection that connects the partition 171 and the plurality of partitions 171 so that the plurality of partitions 171 rotate integrally around the axes of the first and second inner ring bodies 115 (1) and 115 (2). Part 173.

According to the drive mechanism 100A having such a configuration, the rotational power operatively input from the drive source to the retainer 170 is transmitted from the first rolling element 150 (1) to the first inner ring body 115 (1). Between the first transmission path reaching the pump shaft 20 via the second rolling element 150 (2) and the second transmission path reaching the pump shaft 20 via the second inner ring body 115 (2). It is transmitted to the pump shaft 20 through two parallel transmission paths.
Therefore, it is possible to increase the torque of the rotational power that can be transmitted in a variable speed as compared with the conventional drive mechanism.

  In this embodiment, as shown in FIG. 2, the cage 170 is further connected to the connecting portion 173 so as to rotate around the axis of the inner ring body 115 together with the connecting portion 173. The shaft 175 is configured to receive rotational power from the drive source.

One of the inner ring body 115 and the outer ring body 135 (in the present embodiment, the second outer ring body 135 (2)) is pressed along the axial direction by the preloading means 200, and the inner ring body 115 and the A shim 160 is interposed between a pair of the other outer ring body 135 (in the present embodiment, the first and second inner ring bodies 115 (1) and 115 (2)).
In the present embodiment having such a configuration, the axial transmission force applied to the second outer ring body 135 (2) by the preloading means 200 is transmitted through the shim 160 to the second transmission mechanism 145A (2). To the first transmission mechanism 145A (1), so that a preload required for power transmission is generated in both the second transmission mechanism 145A (2) and the first transmission mechanism 145A (1). It has become.

  Specifically, in the present embodiment, the second outer ring body 135 (2) is accommodated in a transmission case 300A provided in the drive mechanism 100A so as to be movable in the axial direction while being non-rotatable about the axis. .

The second inner ring body 115 (2) and the first inner ring body 115 (1) are incapable of relative rotation around the axis with respect to the pump shaft 20 in a state where the second inner ring body 115 (2) and the first inner ring body 115 (1) are in direct or indirect contact with each other. However, relative movement is possible in the axial direction.
The first outer ring body 135 (1) is housed in the transmission case 300A so as not to rotate about the axis and to move to one side in the axial direction.

  With respect to the first and second transmission mechanisms 145A (1) and 145A (2) installed in such a state, the preload means 200 moves the second outer ring body 135 (2) to one side in the axial direction. It is comprised so that it may press.

  The pressing force applied to the second outer ring body 135 (2) by the preload means 200 toward the one axial side is the outer angle groove 136 of the second outer ring body 135 (2) that is movable in the axial direction. The second inner ring body 115 (2) is connected to the second inner ring body 115 (2) via the second rolling element 150 (2) and the inner angle groove 116 of the second inner ring body 115 (2) which is movable in the axial direction. It is transmitted as a force that presses the inner ring body 115 (2) to one side in the axial direction.

The pressing force to one side in the axial direction transmitted to the second inner ring body 115 (2) is applied to the first inner ring body 115 (1) that is movable in the axial direction via the shim 160. The pressing force to one side in the axial direction transmitted to the first inner ring body 115 (1) is transmitted as a force pressing the body 115 (1) toward the one side in the axial direction, and the first inner ring body 115 (1) is transmitted to the first inner ring body 115 (1). The first outer ring is prevented from moving to one side in the axial direction through the inner angle groove 116, the first rolling element 150 (1) and the outer angle groove 136 of the first outer ring body 135 (1). It is transmitted to the body 135 (1) as a force that presses the first outer ring body 135 (1) toward the one side in the axial direction.
Thus, a preload required for power transmission is generated in the first and second transmission mechanisms 145A (1) and 145A (2).

  Here, in the present embodiment, as shown in FIG. 2, a ring-shaped inner collar member 120 is relative to each of the first and second inner ring bodies 115 (1) and 115 (2) around the axis. It is inserted so that it cannot rotate and cannot move relative to the axial direction.

  That is, the inner ring assembly 125 (first inner ring assembly 125 (1)) in which the first inner ring body 115 (1) and the inner collar member 120 fitted into the first inner ring body 115 (1) are integrated is formed. Forming.

Similarly, an inner ring assembly 125 (second inner ring assembly 125 (2)) in which the second inner ring body 115 (2) and the inner collar member 120 fitted into the second inner ring body 115 (2) are integrated. Is forming.
The inner collar member 120 is fitted into the inner ring body 115 by, for example, press fitting, shrink fitting, cold fitting, or the like.

  The inner collar member 120 is engaged with an outer peripheral surface of a rotary shaft (the pump shaft 20 in the present embodiment) to which the inner ring body 115 is coupled so as not to be relatively rotatable around the axis and movable in the axial direction. A central hole having a surface 122a, an outer peripheral surface 122b engaged with an inner peripheral surface of the inner ring body 115, and the inner collar member 120 with respect to the rotational shaft in a state where the rotational shaft is inserted into the central hole. And an engagement structure that is relatively non-rotatable about the axis and capable of relative movement in the axial direction.

  In the present embodiment, as shown in FIG. 2, the engagement structure is a spline structure provided on the inner peripheral surface 122a.

  That is, a spline structure is provided on the outer peripheral surface of the input end 21 of the pump shaft 20, and a spline corresponding to the spline structure of the pump shaft 20 is provided on the inner peripheral surface 122 a of the central hole of the inner collar member 120. A structure is provided.

  According to the first and second transmission mechanisms 145A (1) and 145A (2) according to the present embodiment, the first and second inner ring bodies 115 (1) and 115 (2) are connected to the rotating shaft (the main shaft). In the embodiment, it is possible to easily and surely realize a state in which the pump shaft 20) is relatively non-rotatable around the axis and is relatively movable in the axial direction.

  According to the state, power transmission (friction) loss between the first and second inner ring bodies 115 (1), 115 (2) and the rotating shaft (the pump shaft 20) is prevented or reduced, Preload load can be set accurately.

  As shown in FIGS. 1 and 2, the drive mechanism 100A further permits external access to the first and second inner ring bodies 115 (1), 115 (2) and the retainer 170, A transmission case 300 </ b> A that accommodates the first transmission mechanism 145 </ b> A (1), the second transmission mechanism 145 </ b> A (2), and the cage 170 is provided.

In the transmission case 300A, the retainer 170 can be operatively connected to the drive source, and the inner ring bodies 115 (1) and 115 (2) are directly or indirectly connected to the pump shaft 20 so as not to be relatively rotatable. In this state, it is configured to be detachably connected to the HST case 10 via a fastening member 90 such as a bolt.
The insertion hole of the fastening member 90 is provided with sealing means (not shown) for preventing oil from leaking out from the transmission case 300A. The sealing means can be installed between the head of the fastening member 90 and the bottom surface of the through-hole of the insertion hole, or installed so as to cover the opening end of the insertion hole. Is also possible.

  In the present embodiment, the first and second outer ring bodies 135 (1) and 135 (2) are configured to be non-rotatable around the axis line in a state where the outer peripheral surface is in contact with the inner peripheral surface of the transmission case 300A. It is accommodated in the transmission case 300A.

  Specifically, at least the second outer ring body 135 (2) pressed to one side in the axial direction by the preload means 200 is movable in the axial direction.

On the other hand, as long as the movement of the first outer ring body 135 (1) to the one side in the axial direction is prevented, the first outer ring body 135 (1) can be moved to the other side in the axial direction, and cannot move in the axial direction. It is also possible.
In the present embodiment, the first outer ring body 135 (1) moves to one axial direction side by engaging an end face on one axial side with a stop portion 360 provided on the transmission case 300A. Is prevented.

  In the present embodiment, as shown in FIG. 2, the transmission case 300 </ b> A is provided with a peripheral wall 310 </ b> A and an axial hole 331 that closes one axial direction side of the peripheral wall 310 </ b> A and through which the pump shaft 20 is inserted. And a second end wall 350 that closes the other axial side of the peripheral wall 310A and is provided with an access opening 351 for the retainer 170.

  In the present embodiment, the shaft portion 175 of the cage is rotated about the axis by the bearing member 355 in a state where the shaft portion 175 extends outwardly through the access opening 351 provided in the second end wall 350. The rotary power from the drive source can be operatively input to the shaft portion 175.

  As shown in FIG. 2, the peripheral wall 310 </ b> A allows the first and second outer ring bodies to move while allowing the second outer ring body 135 (2) to be axially pressed by at least the preload means 200. 135 (1), 135 (2) has an engaging surface 311 that engages directly or indirectly with the outer peripheral surface.

  The engagement surface 311 terminates at a position on one side in the axial direction from the second end wall 350, and the peripheral wall 310A further extends from the end on the other side in the axial direction of the engagement surface 311 to the rotation shaft. The mounting surface 312 extends outward in the radial direction with respect to the axis of the (pump shaft 20) and faces the other side in the axial direction.

In the present embodiment, the peripheral wall 310A is formed by the hollow first cylindrical body 320 and the hollow second cylindrical body 325 inserted in the first cylindrical body 320.
Specifically, the second cylindrical body 325 includes a hollow axially extending portion 326 inserted into the first cylindrical body 320, and a radial direction from an end portion on one axial direction side of the axially extending portion 326. A radially extending portion 327, an inner peripheral surface of the axially extending portion 326 forms the engaging surface 311 and an end surface on the other axial direction side of the axially extending portion 326 is The mounting surface 312 is formed, and the radially extending portion 327 forms the stop portion 360.

  The preload means 200 moves in the axial direction on the peripheral wall 310A so that the fixed position in the axial direction can be adjusted in a state where the preload means 200 is directly or indirectly engaged with the other side in the axial direction of the second outer ring body 135 (2). The pressing body 220 is held in a possible manner.

  In the present embodiment, as shown in FIG. 2, the peripheral wall 310A is formed with a screw hole that opens on the mounting surface 312 and extends along the axial direction, and the pressing body 220 includes the transmission mechanism 145 ( 1) After mounting 145 (2), the screw member 210 to be screwed into the screw hole is fixed by tightening. Thereby, the axial movement of the first outer ring body 135 (1) and the second outer ring body 135 (2) is prevented. At that time, the thickness of the shim 160 interposed between the first inner ring body 115 (1) and the second inner ring body 115 (2) is changed and / or the number of the shim 160 is increased or decreased. By doing so, the preload can be adjusted.

  According to the preload means 200, the first and second outer ring bodies 135 (1) and 135 (2) are generated while generating a preload on the first and second transmission mechanisms 145A (1) and 145A (2). It is possible to effectively prevent rotation around the axis against the meaning of the above.

That is, the second outer ring body 135 (2) is pressed to one side in the axial direction while being in contact with the pressing body 220 that is not rotatable.
Accordingly, it is possible to effectively prevent the second outer ring body 135 (2) from rotating against the intention by the frictional force between the pressing body 220 and the second outer ring body 135 (2).

On the other hand, the first outer ring body 135 (1) is prevented from moving to one side in the axial direction by being pressed by the stop portion 360 fixedly installed on the transmission case 300A which is a fixing member.
Therefore, it is possible to effectively prevent the rotation of the first outer ring body 135 (1) against the intention by the frictional force between the stop portion 360 and the first outer ring body 135 (1).

Embodiment 2
Hereinafter, other embodiments of the rolling bearing type transmission mechanism according to the present invention will be described with reference to the accompanying drawings.
FIG. 4 is a cross-sectional view of a drive mechanism 100B including a rolling bearing type transmission mechanism 145B according to the present embodiment, and shows a cross-sectional view corresponding to FIG. 2 of the first embodiment.
In the figure, substantially the same members as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted as appropriate.

  The transmission mechanism 145B according to the present embodiment has a ring-like shape in which the outer ring body 135 (the first and second outer ring bodies 135 (1) and 135 (2)) cannot rotate relative to the axis and cannot move relative to the axis. The outer collar member 180 is different from the transmission mechanism 145A according to the first embodiment in that the outer collar member 180 is externally fitted.

  Specifically, the transmission mechanism 145B according to the present embodiment includes the inner ring body 115, the inner collar member 120 fitted in the inner ring body 115, the rolling element 150, the outer ring body 135, and the outer ring body. 135 and the outer collar member 180 fitted on the outside.

  As shown in FIG. 4, in the drive mechanism 100B, the two transmission mechanisms 145B are arranged in series along the axial direction.

  In the present embodiment, of the two transmission mechanisms 145B, the transmission mechanism 145B (hereinafter referred to as the first transmission mechanism 145B (1) as appropriate) arranged on one side in the axial direction is the inner angle groove 116. Is directed to the other side in the axial direction and radially outward, and the outer angle groove 136 is disposed in a posture toward the one side in the axial direction and radially inward.

  On the other hand, of the two transmission mechanisms 145B, the transmission mechanism 145B (hereinafter referred to as the second transmission mechanism 145B (2) as appropriate) disposed on the other side in the axial direction is the first transmission mechanism 145B (1). In a posture reversed in the axial direction, that is, the inner angle groove 116 faces one side in the axial direction and radially outward, and the outer angle groove 136 faces the other side in the axial direction and radially inward. ing.

  In the present embodiment, an outer ring assembly 185 (first outer ring assembly) in which the first outer ring body 135 (1) and the outer collar member 180 externally fitted to the first outer ring body 135 (1) are integrated. 185 (1)).

Similarly, an outer ring assembly 185 (second outer ring assembly 185 (2)) in which the second outer ring body 135 (2) and the outer collar member 180 fitted on the second outer ring body 135 (2) are integrated. ) Is formed.
The outer fitting of the outer collar member 180 to the outer ring body 135 is performed by, for example, press fitting, shrink fitting or cold fitting.

  The outer collar member 180 includes a central hole having an inner circumferential surface 182a that engages with the outer circumferential surface of the outer ring body 135, an outer circumferential surface 182b that engages with the inner circumferential surface of the fixing member, and the outer collar member 180. An engagement structure is provided for engaging the outer collar member 180 with the fixing member so as not to rotate about the axis and to move in the axial direction in a state of being inserted into the fixing member.

  In the present embodiment, as shown in FIG. 4, the engagement structure is a spline structure provided on the outer peripheral surface 182b.

  That is, the drive mechanism 100B permits the first transmission mechanism 145B (1) and the second transmission mechanism 145B (2) while allowing external access to the first and second inner ring bodies 115 and the retainer 170. ) And a transmission case 300 </ b> B for housing the cage 170.

  As shown in FIG. 4, the transmission case 300 </ b> B is engaged with an outer peripheral surface 182 b of the outer collar member 180 that is externally fitted to the first and second outer ring bodies 135 (1) and 135 (2). A peripheral wall 310B having a surface 311B, a first end wall 330 that closes one axial direction side of the peripheral wall 310B and is provided with an axial hole 331 through which the pump shaft 20 is inserted, and the other axial direction side of the peripheral wall 310G And a second end wall 350 provided with an access opening 351 for the retainer 170.

As shown in FIG. 4, the engagement surface 311B is provided with a spline structure.
A spline structure corresponding to the spline structure of the engaging surface 310B is provided on the outer peripheral surface 182b of the outer collar member 180, and the outer peripheral surface 182b of the outer collar member 180 is engaged with the engaging surface 310B. By combining the first and second outer ring assemblies 185 (1) and 185 (2), it is possible to easily and reliably realize a state where the first and second outer ring assemblies 185 (1) and 185 (2) cannot rotate around the axis and can move in the axial direction.

  According to the said state, a friction loss does not generate | occur | produce between the said holder | retainer 170 and said 1st and 2nd inner ring body 115 (1), 115 (2), and it can improve power transmission efficiency.

  Here, a configuration for generating a preload in the first and second transmission mechanisms 140B (1) and 145B (2) will be described.

  The drive mechanism 100B includes preloading means 450 that presses the first and second inner ring bodies 115 (1) and 115 (2) in directions close to each other.

As shown in FIG. 4, the pump shaft 20 is formed with a screw hole 27 extending in the axial direction with one end portion opened to the end face.
As shown in FIG. 4, the preload means 450 includes a screw member 460 that is screwed into the screw hole 270, a base end portion to which the screw member 460 is engaged, and a radially outward direction from the base end portion. A pressing body 465 that includes a distal end portion that extends and engages directly or indirectly with the other axial side of the second inner ring body 115 (2), and an end face on one axial direction side of the first inner ring body 115 (1). And an engaging portion 470 provided on the pump shaft 20 so as to engage directly or indirectly.

  In the present embodiment, the pressing body 465 is disposed on the other axial side of both the inner collar member 120 fitted into the second inner ring body 115 (2) and the second inner ring body 115 (2). Is engaged.

On the other hand, the engaging portion 470 is engaged with one side in the axial direction of the inner collar member B fitted into the first inner ring body 115 (1).
Specifically, the inner collar member 120B fitted into the first inner ring body 115 (1) has a flange portion 123 that engages with an end surface on one axial direction side of the first inner ring body 115 (1). The engaging portion 470 is configured not to engage with the first inner ring body 115 (1) but to engage only with the inner collar member 120B.

  In the preload means 450, the first and second inner ring bodies 115 (1) and 115 (2) are pushed in directions close to each other in the axial direction by screwing the screw member 460 into the screw hole 27. Pressure is applied.

  The first inner ring body 115 (1) pressed to the other axial side by the preload means 450 faces the outer circumferential surface engaged with the first rolling element 150 (1) on the other axial side and radially outward. On the other hand, the first outer ring body 135 (1) fitted into the outer collar member 180, which has an inner angle groove 116 and engages with the peripheral wall 310B so as to be movable in the axial direction, is the first rolling element 150 ( 1) An outer angle groove 136 facing one side in the axial direction and inward in the radial direction is provided on the inner peripheral surface engaged with 1).

  Thereby, the pressing force on the other axial side applied to the first inner ring body 115 (1) by the preloading means 450 is the inner angle groove 116, the first rolling element 150 (1), and the outer angle groove. Via 136, the first outer ring body 135 (1) is transmitted to the first outer ring body 135 (1) as a force pressing the other side in the axial direction.

  On the other hand, the second inner ring body 115 (2) pressed toward the one axial side by the preload means 450 is axially one side and radially outward on the outer peripheral surface engaged with the second rolling element 150 (2). On the other hand, the second outer ring body 135 (2) fitted into the outer collar member 180 that engages with the peripheral wall 310B so as to be movable in the axial direction is the second rolling element. An outer angle groove 136 facing the other side in the axial direction and inward in the radial direction is provided on the inner peripheral surface engaged with 150 (2).

  Accordingly, the pressing force on one side in the axial direction applied to the second inner ring body 115 (1) by the preloading means 450 is the inner angle groove 116, the second rolling element 150 (2), and the outer angle groove. Via 136, it is transmitted to the said 2nd outer ring body 135 (2) as a force which presses the said 2nd outer ring body 135 (2) to the axial direction one side.

Here, in the present embodiment, as shown in FIG. 4, the first and second outer ring assemblies 185 (1) and 185 (2) are pressed against each other to prevent axial movement. It is arranged so that.
In the illustrated embodiment, the first and second outer ring assemblies 185 (1) and 185 (2) are disposed so as to abut against each other via a shim 160.

  With this configuration, the pressing force applied to the first inner ring body 115 (1) by the preloading means 450 toward the other side in the axial direction generates a preload for the first transmission mechanism 145 (1), and the preload The pressing force applied to the second inner ring body 115 (2) by the means 450 toward one side in the axial direction generates a preload for the second transmission mechanism 145 (2). In this configuration, the preload can be adjusted by changing the thickness of the shim 160 and / or increasing or decreasing the number of the shims 160.

Embodiment 3
Hereinafter, still another embodiment of the rolling bearing type transmission mechanism according to the present invention will be described with reference to the accompanying drawings.
FIG. 5 is a sectional view of a drive mechanism 100C including a rolling bearing type transmission mechanism 145C according to the present embodiment, and is a sectional view corresponding to FIG. 2 of the first embodiment and FIG. 4 of the second embodiment. Indicates.
FIG. 6 is a cross-sectional view taken along the line VI-VI in FIG.
In the figure, substantially the same members as those in the first and second embodiments are denoted by the same reference numerals, and the description thereof is omitted as appropriate.

  The transmission mechanism 145C according to the present embodiment is different from the transmission mechanism 145B according to the second embodiment in that the outer collar member 180 is changed to an outer collar member 180 '.

  The outer collar member 180 ′ is different from the outer collar member 180 in that the outer collar member 180 ′ is engaged with the fixed member so that the outer collar member 180 ′ is engaged with the fixed member so that the outer collar member 180 ′ cannot rotate about the axis and is movable in the axial direction. It is different.

  That is, in the second embodiment, the engagement surface 311B of the transmission case 300B is provided with a spline structure, and the outer collar member 180 is formed on the outer peripheral surface 182b with the spline structure of the engagement surface 311B. It has a corresponding spline structure.

  Instead, in the present embodiment, the outer collar member 180 ′ is engaged with the fixed member by the pin member 190 so that it cannot rotate about the axis and can move in the axial direction.

  Specifically, the drive mechanism 100C includes a transmission case 300C instead of the transmission case 300B as compared with the drive mechanism 100B.

The transmission case 300C is different from the transmission case 300B in that the engagement surface 311B has a groove that opens radially inward and extends along the axial direction.
The outer collar member 180 'has a groove on the outer peripheral surface 182b facing the groove of the engagement surface 311B.

  The pin member 190 is inserted into an engagement hole along the axial direction, which is formed by a groove in the engagement surface 311B and a groove in the outer peripheral surface 182b of the outer collar member 180 ′. The outer collar member 180 ′ is not rotatable about the axis and is movable in the axial direction with respect to the transmission case 300C.

According to such a configuration, it is possible to simplify the processing of the engagement structure for engaging the outer collar member 180 ′ with the fixed member so as not to rotate about the axis but to move in the axial direction.
In the present embodiment, only one pin member 190 is provided, but it is also possible to provide a plurality of pin members 190 in the circumferential direction.

20 Pump shaft (rotary shaft)
115 (1), 115 (2) First and second inner ring body 116 Inner angle groove 120 Inner collar member 135 (1), 135 (2) First and second outer ring body 136 Outer angle groove 145A (1), 145A (2) Rolling bearing type transmission mechanism 145B (1), 145B (2) Rolling bearing type transmission mechanism 150 (1), 150 (2) First and second rolling elements 170 Cage 180 Outer collar member 300A, 300B Transmission case (Fixing member)

Claims (5)

The inner ring body that is not rotatable relative to the rotation axis around the axis, the outer ring body that surrounds the inner ring body such that a gap exists between the inner ring body in the radial direction, and the inner ring body and the outer ring body A plurality of rolling elements formed on the outer circumferential surface of the inner ring body and the inner circumferential surface of the outer ring body, which are in sliding contact with the rolling elements, respectively, and inner angle grooves facing each other with the rolling elements interposed therebetween, and A rolling bearing type transmission mechanism provided with an outer angle groove,
A ring-shaped inner collar member fitted in the inner ring body so as not to rotate relative to the axis and to move in the axial direction;
The inner collar member is configured to be supported by extrapolation on the rotating shaft, and the inner collar member is supported on the rotating shaft with the inner collar member being attached to the rotating shaft. A rolling bearing type transmission mechanism characterized in that an engagement structure is provided that is relatively non-rotatable about an axis and capable of relatively moving in an axial direction. An outer collar member in the form of a ring that is fitted around the outer ring body so as not to rotate relative to the axis and to move in the axial direction;
The outer collar member is configured to be inserted into a non-rotatable fixing member, and the outer collar member is inserted into the fixing member in a state where the outer collar member is inserted into the fixing member. The rolling bearing type transmission mechanism according to claim 1, wherein an engagement structure is provided that engages with each other so as not to rotate about the axis and to be movable in the axial direction. The inner ring body that is not rotatable relative to the rotation axis around the axis, the outer ring body that surrounds the inner ring body such that a gap exists between the inner ring body in the radial direction, and the inner ring body and the outer ring body A plurality of rolling elements formed on the outer circumferential surface of the inner ring body and the inner circumferential surface of the outer ring body, which are in sliding contact with the rolling elements, respectively, and inner angle grooves facing each other with the rolling elements interposed therebetween, and A rolling bearing type transmission mechanism provided with an outer angle groove,
An outer collar member in the form of a ring that is externally fitted to the outer ring body so as not to rotate relative to the axis and to move in the axial direction;
The outer collar member is configured to be inserted into a non-rotatable fixing member, and the outer collar member is inserted into the fixing member in a state where the outer collar member is inserted into the fixing member. A rolling bearing type transmission mechanism characterized in that an engagement structure is provided to engage with the shaft so as not to rotate about the axis and to be movable in the axial direction.   4. The rolling bearing transmission mechanism according to claim 1, wherein the engagement structure is a spline structure. Grooves along the axial direction are formed on the opposing surfaces of the outer collar member and the fixing member so as to face each other.
4. The engagement structure according to claim 1, wherein the engagement structure includes an engagement hole defined by a groove of the outer collar member and the fixing member, and a pin inserted through the engagement hole. A rolling bearing type transmission mechanism according to claim 1.

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