JP4265464B2 - Fillet rolling processing equipment - Google Patents

Description

  The present invention relates to a fillet rolling processing device for fillet rolling processing (fillet roll processing or fillet roll processing), and particularly to a journal portion of an internal combustion engine crankshaft and a fillet groove portion (inner corner round portion) of a crankpin portion. The present invention relates to a fillet rolling processing apparatus that is considered so that the pressure to be applied to the fillet groove portion can be changed in the circumferential direction of the fillet groove portion when performing the fillet rolling processing to apply compressive residual stress.

  For example, in a fillet rolling processing device for a crankshaft, as is well known, a fillet roller made of cemented carbide or high-speed material is pressed against a fillet groove of a journal portion or a crankpin portion while being pressed with a pressure of several kN or more. The purpose of this is to improve the fatigue strength of the corresponding part by applying roll processing (plastic processing) by applying a compressive residual stress.

  In this case, there is a great correlation between the applied pressure to be applied and the fatigue strength of the crankshaft, and it becomes possible to produce a crankshaft that is excellent in fatigue strength as a higher applied pressure is applied.

  In the conventional general fillet rolling processing apparatus represented by Patent Document 1, it is basically applied to the same pressure over the entire circumference of the fillet groove to be processed. For example, as shown in FIG. Thus, when the crankshaft S is actually incorporated in the engine, a large load is applied to the bottom portion side of the crankpin portion P and cracks Cr are likely to occur, and the bottom portion is the bottom portion on the top portion side opposite to the bottom portion side. Since a larger load is not applied to the part side, the product functions even if the bottom side fillet groove part F is processed with a larger applied pressure and the top part side fillet groove part F is subjected to a roll process with a relatively smaller applied pressure. There is no problem on. Note that the bottom side of the crankpin portion P is on the counterweight Cw side when it is assumed that the crankpin portion P is bisected by a plane parallel to and passing through the axis as shown in FIG. And the top of the region sandwiched between the counterweights Cw and Cw (position of 0 ° in FIG. 14), the top portion side being opposite to the bottom portion side (position of 180 ° in FIG. 14) Say.

  In other words, the pressure force to be applied to the fillet groove portion F is actively changed in the circumferential direction of the fillet groove portion F, and as described above, the fillet groove portion F on the bottom side has a larger pressure and crack Cr enters. If roll processing is performed in an easy direction, it is possible to expect a longer life of the roller, and it is preferable in terms of improving the shape accuracy of the crankshaft S.

Therefore, as described above, the hydraulic cylinder, which is a pressurizing force generating means of the fillet roller, according to the rotation phase of the fillet groove F in order to positively change the pressure applied to the fillet groove F in the circumferential direction of the fillet groove F. Japanese Patent Application Laid-Open No. H10-228707 proposes a technique that positively and variably controls the pressure.
Japanese Patent Laying-Open No. 2003-25221 (FIG. 5) Japanese Patent Publication No. 60-17663 (Fig. 2)

  However, in the technique as described in Patent Document 2, even during the fillet rolling process, for example, even if a command to change the applied pressure is output according to the rotational phase position of the fillet groove, a response delay that is a characteristic of the hydraulic circuit is reduced. For this reason, there is a restriction that not only a phase shift is likely to occur between the command side and the actual pressure application position, but also a sufficiently large difference between the high pressure and the low pressure cannot be secured. Therefore, not only the entire equipment becomes complicated and expensive due to the need for complicated control equipment, but also improvement in processing quality cannot be expected, and there is still room for improvement.

  The present invention has been made paying attention to such problems, and in particular, a fillet rolling process in which the pressure to be applied to the fillet groove can be actively and accurately controlled in the circumferential direction of the fillet groove. A device is provided.

  In the first aspect of the present invention, the fillet roller backed up by the backup roller is pressed against the shaft-shaped portion to be processed, and the fillet roller and the backup roller are rotated while the shaft-shaped portion is rotated. It is assumed that the fillet rolling processing apparatus is configured to perform rolling processing on the fillet groove portion of the shaft-shaped portion.

Then, a guide groove is formed on the outer peripheral surface of the backup roller having a diameter larger than that of the fillet roller so as to contact the fillet roller while guiding the guide roller so that the groove width gradually changes in the circumferential direction. During rotation, the roller contact angle between the plane perpendicular to the axis of the fillet roller and the plane perpendicular to the axis of the backup roller is changed according to the change in the groove width of the guide groove , and the backup roller itself is used as a rotating part. A rotation detector for detecting the rotational displacement is provided .

  The shaft-like portion mentioned here assumes a journal portion and a crankpin portion in the crankshaft as exemplified above.

  More specifically, in order to simultaneously process a pair of left and right fillet grooves located at both ends in the longitudinal direction of the shaft-like portion, as shown in claim 2, substantially corresponding to the fillet groove portions at both ends of the shaft-like portion. A pair of left and right fillet rollers arranged in a C-shape are backed up by a common backup roller, and a pair of left and right guide grooves that guide them while contacting the fillet roller are provided on the outer peripheral surface of the backup roller. It is desirable to form the guide grooves together with the partition portions located between the guide grooves, and to form each guide groove so that the groove width gradually changes in the circumferential direction of the backup roller together with the width dimension of the partition portions.

  At the same time, as described in claim 3, it is desirable that the diameter of the guide groove in the backup roller is set to be the same as the diameter of the fillet groove to be processed.

  Therefore, in at least the first and second aspects of the invention, if the fillet roller backed up by the backup roller is pressed against the fillet groove to be processed and the fillet groove is rotated, the fillet roller will be on the backup roller side. The guide groove is guided to the guide groove while being in contact with the back-up roller, and is rotated together with the backup roller to perform a predetermined rolling process on the fillet groove portion.

At that time, as described in claim 3, if it is assumed that both the backup roller and the fillet groove are set to have the same diameter, the backup roller and the fillet groove are interposed between the two. The fillet roller rotates synchronously in a 1: 1 relationship via the fillet roller, and at the same time, the fillet roller changes its roller contact angle in a purely mechanical and autonomous manner according to the change in the groove width of the guide groove in the circumferential direction. It will be. This change in the roller contact angle is nothing but a change in the applied pressure exerted on the fillet groove by the fillet roller, and as a result, the applied pressure continuously changes in the circumferential direction of the fillet groove. The output of the rotation detector is used to match the rotation phase of the fillet groove to be processed with the rotation phase of the backup roller.

According to the first aspect of the present invention, the pressurizing force to be applied to the fillet groove can be arbitrarily and accurately variably controlled in the circumferential direction while having a very compact equipment configuration, and roll processing quality can be controlled. As a result, the life of the fillet roller can be extended. In addition, a change in the roller contact angle of the fillet roller means not only a change in the pressing force but also a change in the direction in which the pressing force is applied, so that the roll processing can be further optimized.
In addition, by providing the rotation detector, the rotation phase of the fillet groove during processing can be matched with the rotation phase of the backup roller, and the occurrence of rotational phase deviation during processing can be prevented in advance. .

  1 and 2 show a schematic configuration of a fillet rolling device for a crankshaft S of an in-line four-cylinder engine as a more specific embodiment of the present invention.

  As shown in FIG. 3 in addition to FIGS. 1 and 2, in this fillet rolling processing apparatus, a work rest cassette 2 provided with a rest roller 3 in addition to a roll cassette 1 mainly composed of fillet rollers 25a and 25b described later is used together. Then, fillet rolling is performed in parallel to the fillet groove portions F at both ends of each journal portion J which is a shaft-shaped portion and the fillet groove portions F at both ends of each crankpin P which is also a shaft-shaped portion. The crankshaft S is rotationally driven in a state where the crankshaft S is supported at both ends by a predetermined chuck 4 and center 5.

  FIG. 2 shows a machining state at the clamp pin portion P. As shown in FIG. 2, the support bracket 7 fixed to the base 6 has an independent swing arm 8 for each crank pin portion P that is a machining portion. Of the pair of upper and lower arms 11 and 12 connected to the upper end of the swing arm 9 so as to be swingable or openable and closable with respect to each other. A part of the lower arm 12 is swingably supported via a hinge pin 13. The pair of arms 11 and 12 are opened and closed in accordance with the expansion and contraction operation of the pressure cylinder (hydraulic cylinder) 14 connected in a bridging manner between the rear ends, and the fillet rolling process is performed with the pressure of the pressure cylinder 14. The time pressure is applied.

  A roll cassette 1 which is a roll cassette device incorporating fillet rollers 25a and 25b, which will be described later, is detachably mounted on the distal end of the upper arm 11, while a pair of front and rear rotations are mounted on the distal end of the lower arm 12. Similarly, a work rest cassette 2 having a rest roller 3 is detachably mounted. As will be described later, the fillet rollers 25a and 25b are in the fillet groove portions F at both ends of the crank pin portion P, and the rest roller 3 is cranked. The fillet rolling process is performed in a state in which the general surface of the pin portion P is in pressure contact with each other.

  4 to 6 show details of the roll cassette 1. The roll cassette 1 is detachably and firmly fixed to the tip of the arm 11 with a pair of upper and lower clamp blocks 15 and mounting bolts 16.

  As shown in FIGS. 4 and 5, a case 20 comprising a substantially flat rectangular case body 17 and a disc-shaped cover plate 19 fixed by screws 18 (however, in FIG. A state in which the cover plate 19 is removed to make it visible is depicted), and a large-diameter backup roller 22 having a short cylindrical shape or a flat cylindrical shape is rotatably accommodated and arranged via a shaft 21a and a needle bearing 21b. In addition, arc-shaped guide grooves 24 for individually receiving and supporting fillet rollers 25a and 25b, which will be described later, are formed in the corners at both ends of the outer peripheral surface of the backup roller 22 to support them. .

  Just below the backup roller 22 are small-diameter fillet rollers 25a and 25b held by a pair of front and rear frame-like retainers 23a and 23b, that is, a pair of left and right fillet rollers 25a and 25b having a smaller diameter than the backup roller 22. The roller contact angle β (see FIG. 5) is inclined so as to have a substantially C-shaped cross section, that is, the axis perpendicular plane of the fillet rollers 25 a and 25 b and the axis perpendicular plane of the backup roller 22. The retainers 23 a and 23 b are positioned and supported by a front cage 26 and a rear cage 27 that are fixed to the case main body 17 by mounting bolts 36.

  More specifically, as shown in FIG. 3, the pair of left and right fillet rollers 25a and 25b has a shape in which one side swells into a disk shape or an abacus ball shape, while supporting the fillet rollers 25a and 25b. A pair of front and rear retainers 23a and 23b are provided with a substantially quarter-arc-shaped roller holding groove 28 for accommodating and supporting the fillet rollers 25a and 25b in an inclined posture as shown in FIGS. The tops of the upper sides of the fillet rollers 25a and 25b are received and positioned in the guide grooves 24 of the backup roller 22, while a part of the lower side of the fillet rollers 25a and 25b is exposed from the roller holding grooves 28 to the outside. Falling from the pair of front and rear retainers 23a, 23b is prevented while facing.

  The roller holding grooves 28 formed in the pair of front and rear retainers 23a and 23b are formed so that the groove width dimension gradually increases upward from the lower end opening as shown in FIG. In addition, a notch groove 29 into which a later-described front cage 26 and rear cage 27 are fitted is formed on the lower surface of each retainer 23a, 23b.

  Thus, as will be described later, the fillet rollers 25a and 25b supported by the pair of front and rear retainers 23a and 23b have a degree of freedom to be tilted and displaced in the roller holding groove 28, so that the fillet rollers 25a and 25b The posture change is allowed within a range formed by the minimum roller contact angle β1 and the maximum roller contact angle β2 with the contact portion with the guide groove 24 on the backup roller 22 side as a fulcrum. In this embodiment, for example, the minimum roller contact angle β1 is set to 30 °, and the maximum roller contact angle β2 is set to 45 °.

  That is, as shown in FIG. 7A, when the fillet rollers 25a and 25b are at the minimum roller contact angle β1, the posture of the fillet rollers 25a and 25b is restricted by one wall surface of the roller holding groove 28, and the other When the fillet rollers 25a and 25b are at the maximum roller contact angle β2, the posture of the fillet rollers 25a and 25b is regulated by the other wall surface of the roller holding groove 28.

  The pair of front and rear retainers 23 a and 23 b are supported by the front cage 26 and the rear cage 27 attached to the lower surface of the case 20 as described above, and the front cage 26 and the rear cage 27 are provided with mounting bolts 36 and elongated holes 30. In addition, adjustment bolts 31 and 32 are fixed to the case body 17 so that the position can be adjusted.

  As shown in FIG. 6, protrusions 33, 33 or 34, 34 are formed at both ends of the front cage 26 and the rear cage 27 that face each other and directly contact the retainers 23 a, 23 b. The front and rear retainers 23a, 23b are positioned and supported by fitting these projections 33, 33 and 34, 34 into the notch grooves 29 (see FIG. 7) on the lower surface side of the retainers 23a, 23b. ing.

  The backup roller 22 described above rolls while contacting the pair of left and right fillet rollers 23a, 23b while being rotatably supported by the case 20, and is processed while guiding these fillet rollers 23a, 23b. Since the reaction force is borne, as shown in FIGS. 8 and 9, a pair of fillet rollers 23a and 23b are received on both sides of the entire outer peripheral surface of the central partition wall 35. For this purpose, two guide grooves 24 having a substantially arc-shaped cross section are formed.

  While the axial length of the backup roller 22 is constant in each part, the width dimension W of the partition wall part 30 gradually increases or decreases in the circumferential direction as shown in FIG. 8C. As a result, the width dimension (groove width) G of the two guide grooves 24 located on both sides of the partition wall 35 is also gradually increased in the circumferential direction. Alternatively, it is set to continuously change so as to decrease.

  That is, while receiving the fillet rollers 23a and 23b as shown in FIGS. 12 and 13 with a rounded inner corner formed by the partition wall 35 at the center and the bottom surfaces of the pair of left and right guide grooves 24, the roller contact angle β1 is received. Alternatively, β2 is regulated. In addition, the diameter of the groove bottom face of a pair of guide groove 24 is preset so that it may become equal to the diameter of the fillet groove part F by the side of the crankpin part P used as a process target.

  Thus, the width dimension W of the partition wall 35 and the width dimension G of the guide groove 24 are positively and continuously changed in the circumferential direction via the pair of fillet rollers 23a and 23b during the fillet rolling process. 14 to continuously change the roller contact angle β of each of the fillet rollers 23a and 23b in accordance with the rotational phase of the backup roller 22 that rotates with the fillet rollers 23a and 23b. As shown as a relationship between the rotational phase of the crankpin portion P and the applied pressure, when the backup roller 22 is expanded, the width dimension W of the partition wall portion 35 and the groove width G of the pair of guide grooves 24 are so-called sinusoidal shapes. It is set to be.

  For example, when attention is paid to the partition wall portion 35 at the center of the backup roller 22, the position of the partition wall portion 35 is shifted by 180 degrees in the circumferential direction of the backup roller 22, that is, as shown in FIGS. A portion having a width dimension W1 is defined as a maximum width dimension portion P1, and a portion having a width dimension W2 that is 180 degrees out of phase from the maximum width dimension portion P1 (an opposite side position) is defined as a minimum width dimension portion P2. Assuming that the backup roller 22 is expanded, the maximum width dimension portion P1 and the minimum width dimension portion P2 are linearly connected, so that the width dimension W of the partition wall portion 35 is as shown by the characteristic curve in FIG. It is set to continuously change in the circumferential direction within the range of W1 and W2. These are the same for the guide grooves 24 on both sides of the partition wall 35, and the relative positional relationship between the maximum groove width and the minimum groove width is opposite to that of the partition 35. Only.

  Accordingly, as will be described later, the fillet rollers 23a and 23b are in pressure contact with the fillet groove portion F of the crankpin portion P to be processed, and the backup roller 22 is in pressure contact with the fillet rollers 23a and 23b. Since processing is performed while the three parties rotate synchronously, the fillet groove portion F and the backup roller 22 having the same diameter are rotated in a 1: 1 relationship via the fillet rollers 23a and 23b. The roller contact angle β of the fillet rollers 23a and 23b shown in 5 and 7 continuously changes between the minimum roller contact angle β1 and the maximum roller contact angle β2.

  That is, even if the pressure of the pressure cylinder 14 shown in FIG. 2 is constant, the roller contact angle β of the fillet rollers 23a and 23b increases as will be described later (the inclination of the fillet rollers 23a and 23b increases). ), The pressure applied to the fillet groove F by the fillet rollers 23a and 23b is actually increased, and when the bottom side of the fillet groove F in the crankpin portion P is processed as shown in FIGS. The fillet rollers 25a and 25b are opposed to each other so that the bottom width side thereof faces the minimum width dimension portion P2 (FIG. 10) on the partition wall 35 side of the backup roller 22 and the fillet groove portion F of the crankpin portion P is formed. Of these, when machining the top part side, the top part side and the barb are sandwiched between the fillet rollers 25a and 25b. The phase adjustment is performed in advance so that the maximum width dimension portion P1 (FIG. 10) on the partition wall 35 side of the cup-up roller 22 faces, and the bottom portion of the fillet groove portion F in the crankpin portion P shown in FIG. So that the pressure applied to the fillet groove F gradually changes between the two positions so that the pressure is the largest on the side and the pressure on the top opposite to the bottom is minimized. It is set to.

  Further, as shown in FIGS. 8 to 10, a tooth profile portion 37 is integrally formed with a concavo-convex portion having an equal pitch on the entire circumference in the central portion in the width direction of the partition wall portion 35, and as shown in FIG. A reference protrusion 38 serving as a tooth profile is formed by extending one specific protrusion of the tooth profile 37 in the width direction of the backup roller 22. The tooth profile 37 and the reference projection 38 are formed as a part of a rotation detector 39 such as a so-called rotary encoder or pulse generator having the backup roller 22 itself as a rotating part. 13, the proximity sensors 40 or 41 that are independent from each other face the tooth profile portion 37 and the reference projection portion 38 from the case 20 side so as to face each other in a non-contact manner. Both proximity sensors 40 and 41 are offset by a predetermined amount in the width direction of the backup roller 22.

  As shown in FIG. 12, the tooth profile portion 37 and one proximity sensor 40 form a rotation detecting function portion 42 of the backup roller 22, whereby the proximity sensor 40 is backed up along with the rotational displacement of the backup roller 22. A pulse signal corresponding to the rotational displacement during one rotation of the roller 22 is output.

  On the other hand, as shown in FIG. 13, the single reference protrusion 38 (see FIGS. 10 and 11) and the other proximity sensor 41 form the origin detection functioning portion 43 of the backup roller 22, and thereby the proximity sensor In response to the rotational displacement of the backup roller 22, one pulse signal 41 is output for each rotation of the backup roller 22.

  The output of the rotation detector 39 configured as described above is used to make the rotation phase of the fillet groove F to be processed and the rotation phase of the backup roller 22 coincide with each other, as will be described later.

  Therefore, according to the present embodiment, as shown in FIGS. 4 and 5 in addition to FIG. 2, the pair of rest rollers 3 on the workrest cassette 2 side is pressed against a portion other than the fillet groove portion F of the crankpin portion P. The pair of fillet rollers 25a and 25b on the roll cassette 1 side are pressed against the fillet groove portions F at both ends of the crank pin portion P, and the crank pin portion P is substantially sandwiched between the work rest cassette 2 and the roll cassette 1 The crankpin portion P and the entire crankshaft S are driven to rotate. The rest roller 3 rotates synchronously with the rotation of the crankshaft S, and the pair of left and right fillet rollers 25a and 25b rotate synchronously so as to be rotated together with the backup roller 22 while being backed up by the backup roller 22. The fillet groove F is subjected to fillet rolling. That is, each fillet roller 25a, 25b contributes to the improvement of the fatigue limit stress of the fillet groove F by applying a cold rolling process to the fillet groove F and applying an internal compressive stress.

  During such fillet rolling, the pair of fillet rollers 25a and 25b are backed up at the inner rounded corner portion formed by the partition wall portion 35 of the backup roller 22 and the guide groove 24 as shown in FIGS. The fillet groove portion F and the backup roller 22 having the same diameter through the fillet rollers 25a and 25b are synchronously rotated in a 1: 1 relationship via the fillet rollers 25a and 25b. Inside, the roller contact angle β of each fillet roller 25a, 25b changes continuously according to the width dimension W of the partition wall 35, that is, according to the groove width G of the guide grooves 24 on both sides of the partition wall 35. become.

  More specifically, if the width dimension W of the partition wall portion 35 of the backup roller 22 where the fillet rollers 25a and 25b are backed up is large, the roller contact angle β of the fillet rollers 25a and 25b becomes small and the fillet roller 25a. 25b stands up as shown in FIG. 12, and if the width W of the partition wall portion 35 where the fillet rollers 25a, 25b are backed up is small, the roller contact angle β of the fillet rollers 25a, 25b increases. The fillet rollers 25a and 25b are inclined as shown in FIG.

  As shown in FIG. 10 in addition to FIGS. 12 and 13, during the synchronous rotation of the fret portion F, the fillet rollers 25a and 25b, and the backup roller 22 that are the processing target portions, the width dimension of the partition wall portion 35 is maximum with W1. The maximum width dimension portion P1 to be equal to the top portion side of the crankpin portion P, and the minimum width dimension portion P2 having the minimum width dimension of the partition wall portion W2 to coincide with the bottom portion side of the crankpin portion P. Since the both phases are set in advance, the roller contact angle β becomes the maximum roller contact angle β2 on the bottom side of the crankpin portion P, and the inclination of the fillet rollers 25a and 25b is increased. The roller contact angle β becomes the minimum roller contact angle β1 on the top portion side of the pin portion P, and the postures of the fillet rollers 25a and 25b are standing upright. Further gradually becomes continuously varying it between a maximum roller contact angle β2 and the minimum roller contact angle β1 is between the bottom portion side and the top side.

  In this case, even if the pressure clamping force between the workrest cassette 2 and the roll cassette 1 by the pressure cylinder 14 shown in FIG. 2 is constant, each fillet roller 25a, 25b finally exerts on the fillet groove F. The applied pressure depends on the roller contact angle β of the fillet rollers 25a and 25b, and the applied pressure exerted by the fillet rollers 25a and 25b on the fillet groove F increases as the roller contact angle β increases.

This is because each fillet groove portion is defined as F ₁ as the pressure force actually applied to the fillet groove portion F, F ₀ as the pressure clamping force between the cassettes 1 and 2 based on the output of the pressure cylinder 14, and β as the roller contact angle. The pressing force F ₁ actually applied to F can be understood from the following expression (1).

F ₁ = 1/2 × (F ₀ / cos β) (1)
That is, as shown in FIG. 17, the bottom portion side of the clamp pin portion P that requires higher strength can be processed with a larger pressing force than the top portion side.

At the same time, this change in the roller contact angle β also means a change in the direction of action with the pressurizing force F _1, and as is apparent from FIG. 17, the roller contact angle β particularly increases on the bottom portion side of the crankpin portion P. As a result, the acting direction m of the pressing force F ₁ substantially coincides with the direction of occurrence of the crack Cr (the acting direction of the conventional pressing force F ₁ is the m1 direction), and the pressing force can be applied more effectively. .

  Here, at the start of the fillet rolling process as described above, the rotation phase that is the machining start position (rotational direction position) of the crankshaft S and the machining start position (rotational direction position) of each crank pin portion P is also obtained. The rotational phase is known and is preliminarily indexed to the normal position by the indexing function of the crankshaft rotational drive system. At the same time, if each of the crank pin portions P is sandwiched between the work rest cassette 2 and the roll cassette 1 and the rotation detector 39 described above detects the origin position with the reference protrusions 38, the workpiece is processed. The rotational phase of the fillet groove F and the rotational phase of the backup roller 22 are in agreement with each other, and the process immediately shifts to regular processing.

  On the other hand, if the crank pin portion P is sandwiched between the work rest cassette 2 and the roll cassette 1 and the rotation detector 39 described above does not detect the origin position with the reference protrusion 38, the workpiece is processed. The rotational phase of the fillet groove F and the backup roller 22 is shifted.

  Therefore, the pair of upper and lower arms 11 and 12 in FIG. 2 that are independent for each crankpin portion P can be opened and closed independently (the operation of sandwiching the crankpin portion P by the workrest cassette 2 and the roll cassette 1) 2) and can be swung or rotated by a predetermined amount by an external driving means with the hinge pin 9 or 13 shown in FIG. 2 as the center of rotation, so that the fillet groove F to be processed is plastic. If the crank pin portion P is sandwiched between the work rest cassette 2 and the roll cassette 1 with a pressing force that does not cause deformation, the pair of upper and lower arms 11, until the rotation detector 39 detects the origin position with the reference protrusion 38, 12 is rotated at a very low speed. Thereby, the rotational phase of the fillet groove F to be processed and the rotational phase of the backup roller 22 can be made to coincide with each other as described above.

  In a normal continuous machining cycle for the purpose of mass production of the crankshaft S, the rotation direction phase of the crankshaft S, that is, the rotation direction phase of each crank pin portion P is set to the same phase at the machining start position and the machining completion position. Therefore, the phase alignment as described above is not always necessary, and it is sufficient to execute the interrupt process only when a phase shift occurs during continuous machining.

  In addition, after the start of the fillet rolling process, the so-called matching process is performed by using the rotation position detection function of the crankshaft rotation drive system and the rotation detection function unit of the rotation detector 39 described above. The rotational phase of the fillet groove portion F in the crank pin portion P in the center can be made to coincide with the rotational phase of the backup roller 22, and the occurrence of a rotational phase shift during processing can be prevented beforehand.

  In this embodiment, since the processing of the crankpin portion P is the main focus, only the fillet rolling processing of the crankpin portion P has been described, but the fillet rolling processing of each journal portion J is also performed in parallel. Needless to say. In this case, the roll cassette for performing the fillet rolling process of the journal part J is different from the roll cassette 1 for the crankpin part P in that it does not have the function of the rotation detector 39 described above, but the other configuration Is basically the same as the roll cassette 1 for the crankpin portion P.

  Here, the developed shape of the partition wall portion 35 and the guide groove 24 of the backup roller 22 shown in FIGS. 8 to 10 is obtained by transferring a so-called sinusoidal curve-shaped pressure force characteristic curve as shown in FIG. As described above, the developed shape is not necessarily limited to that shown in FIG. For example, as shown in FIG. 15, in the characteristic curve, the vicinity of the position corresponding to the bottom portion and the vicinity of the top portion corresponding to the crankpin portion P may be flattened, or only the vicinity of the position corresponding to the bottom portion may be flattened. Good.

BRIEF DESCRIPTION OF THE DRAWINGS Schematic structure explanatory drawing which shows preferable embodiment of the fillet rolling processing apparatus for crankshafts concerning this invention. Side surface explanatory drawing of FIG. The principal part expanded sectional view which shows the mutual relationship of the fillet groove part used as a process target, and a fillet roller. Explanatory explanatory drawing of the roll cassette in FIG. The expanded sectional view which follows the CC line of FIG. The expanded bottom view of FIG. It is an enlarged view which shows the detail of the retainer of FIG. 6, (A) is the front view, (B) is a bottom view, (C) is a rear view, (D) is along the EE line of the same figure (B). Sectional drawing. It is an enlarged view which shows the detail of the backup roller of FIG. 4, (A) is the top view, (B) is a front view, (C) is a side view. FIG. 9 is a full sectional view of the backup roller of FIG. 8. It is a figure which shows the detail of the backup roller similar to FIG. 8, (A) is the side view seen from the maximum width dimension part side of a partition part, (B) is the side view seen from the minimum width dimension part side of a partition part similarly. . (A) is the Q section enlarged view in (B) of Drawing 8, (B) is a top view of the same figure (A). (A) is sectional drawing which follows the AA line of FIG. 4, (B) is a principal part enlarged view of the same figure (A). (A) is sectional drawing which follows the BB line of FIG. 4, (B) is a principal part enlarged view of the same figure (A). The characteristic curve figure which shows the relationship between the rotation direction phase and pressurization force in the fillet groove part of a crankpin part. The characteristic curve figure which shows the modification of FIG. The characteristic curve figure which shows another modification of FIG. The principal part enlarged view of the crankpin part in a crankshaft.

Explanation of symbols

1. Roll cassette (roll cassette device)
DESCRIPTION OF SYMBOLS 17 ... Case main body 20 ... Case 22 ... Backup roller 24 ... Guide groove 25a, 25b ... Fillet roller 35 ... Bulkhead part 37 ... Tooth profile part 38 ... Reference | standard protrusion part as a tooth profile part 39 ... Rotation detector 40, 41 ... Proximity sensor 42 ... rotation detection function part 43 ... origin detection function part F ... fillet groove part G ... groove width of guide groove P ... crank pin part (shaft-like part)
P1 ... Maximum width dimension part P2 ... Minimum width dimension part W1 ... Maximum width dimension of partition wall part W2 ... Minimum width dimension of partition wall part β ... Roller contact angle β1 ... Minimum roller contact angle β2 ... Maximum roller contact angle

Claims (8)

While the fillet roller backed up by the backup roller is pressed against the shaft-shaped part to be processed, the fillet roller and the backup roller are rotated while the shaft-shaped part is rotated, and rolled to the fillet groove of the shaft-shaped part. A fillet rolling processing device adapted to perform processing,
On the outer circumferential surface of the backup roller having a diameter larger than that of the fillet roller, a guide groove that is in contact with the fillet roller and guides it is formed so that the groove width gradually changes in the circumferential direction,
During rotation of the backup roller, the roller contact angle between the plane perpendicular to the axis of the fillet roller and the plane perpendicular to the axis of the backup roller is changed according to the change in the groove width of the guide groove ,
Furthermore , the fillet rolling processing apparatus characterized by having provided the rotation detector which detects the rotational displacement by using the backup roller itself as a rotation part . A pair of left and right fillet rollers arranged in a substantially C shape corresponding to the fillet groove portions at both ends of the shaft-shaped portion are backed up by a common backup roller,
On the outer peripheral surface of the backup roller, a pair of left and right guide grooves for guiding them while abutting the fillet roller is formed together with a partition wall portion positioned between the guide grooves,
2. The fillet rolling processing apparatus according to claim 1, wherein each guide groove is formed such that the groove width thereof gradually changes in the circumferential direction of the backup roller together with the width dimension of the partition wall.   The diameter of the guide groove in the backup roller is set to be the same as the diameter of the fillet groove part to be processed, and the fillet rolling processing apparatus according to claim 1 or 2.   4. The backup roller and the fillet roller are rotatably accommodated in a common case, respectively, and the backup roller and the fillet roller are cassetteized as a roll cassette device with the case as a base. Fillet rolling processing device according to claim 1.   The fillet rolling processing apparatus according to claim 4, wherein the case includes a rotation detector that detects a rotational displacement of the backup roller itself as a rotating portion.   The said rotation detector is formed with the tooth profile part formed in the outer peripheral surface of the partition part in a backup roller, and the proximity sensor arrange | positioned so as to oppose this tooth profile part. The fillet rolling processing device described.   The rotation detector includes a rotation detection function unit that generates a pulse signal corresponding to the rotational displacement during one rotation of the backup roller, and an origin detection function unit that generates one pulse signal for one rotation of the backup roller. The fillet rolling processing apparatus according to claim 6, wherein: On the outer peripheral surface of the partition wall in the backup roller, a tooth profile for the rotation detection function part and a tooth profile part for the origin detection function part are formed in parallel.
8. The fret rolling processing apparatus according to claim 7, wherein each tooth profile part is provided with an independent proximity sensor separately for each of the rotation detection function part and the origin detection function part.

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