JPH1076450A - Grinding method and grinding device for double cone roller - Google Patents

Abstract

PROBLEM TO BE SOLVED: To manufacture a double cone roller at low cost and high precision by use of double head surface grinding in a contiuous feed grinding method. SOLUTION: A double cone roller W is held on a carrier pocket 10 of a carrier disc 3 in a rotatable condition, and it is inserted and fed between a pair of an upper and a lower grinding wheels 1, 2 facing each other to rotate inversely to each other, so double cone surfaces Wa, Wb of the double cone roller W are fed to get in contact with grinding surfaces 1a, 2a of the grinding wheels 1, 2 for performing simultaneous grinding to both cone surfaces Wa, Wb while the double cone roller W is rotated. The double cone roller W is thus ground by one pass and at high machining precision, thereby the double cone rollers W can be continuously and automatically machined in a mass quantity, with manufacturing cost by mass production machining largely reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method and an apparatus for grinding a double tapered roller, and more particularly, to a double tapered roller suitably used as a rolling element for a thrust force support structure in a scroll compressor, for example. And a grinding technique for simultaneously grinding both conical surfaces.

[0002]

2. Description of the Related Art A scroll type compressor is a kind of rotary compressor, which is small in size, has no valve mechanism, and has continuous fluid compression. Low vibration and high-speed operation,
In recent years, practical application has been actively promoted.

[0003] By the way, this type of compressor is provided with a thrust force support structure which enables the scroll drive. This support structure constitutes a kind of thrust bearing, and a sphere such as a steel ball is used as a rolling element. In such a sphere, since the supporting state is point contact, high-speed long-term There was a problem that the durability was poor in use.

In this regard, as shown in FIG. 5 (a), a scroll compressor having a thrust force support structure has recently been proposed (for example, Japanese Utility Model Laid-Open Publication No. 61-82086, Japanese Unexamined Patent Publication No. 62-107284, etc.).

The basic structure of this compressor is as shown in the figure.
In the housing a, a fixed scroll member c having a spiral body b is fixed, and a revolving scroll member e having a spiral body d meshing with the spiral body b is supported by a thrust force support structure f so as to be capable of turning or revolving. The orbiting scroll member e is drivingly connected to a driving source (not shown) via a crank pin g.

The support structure f is in the form of a type of thrust bearing as described above, and a plurality of recesses h and i are provided on the inner surface of the housing a and the opposing surface of the revolving scroll member e, respectively, and These recesses h, i
A bi-conical rolling element (bi-conical roller) W is interposed so as to be able to roll.

[0007] By the rotation of the crank pin g, the revolving scroll member e is turned into the stationary scroll member c.
The fluid gas sucked from the suction port j is revolved without rotating, and compressed by the compression chamber formed between the spiral bodies b and d, and then discharged from the discharge port k. Have been.

In this case, as shown in the schematic diagram of FIG. 5 (b), the outer peripheral surfaces Wa and Wb of the double tapered roller W have concave portions h and i.
The rolling motion is performed in a line contact state with the flat bottom surfaces m and n, and the durability is remarkably improved as compared with the conventional rolling element made of a sphere, and it can withstand long-term use at high speed. There is an advantage of gaining.

[Problems to be solved by the invention]

However, in spite of having such excellent durability, the scroll type compressor having such a thrust force supporting structure f has not been established with the grinding technology of the double tapered roller W. For this reason, the fact is that it has not yet been put to practical use.

That is, the double conical roller W is an abacus spherical bearing element in which the upper and lower outer peripheral surfaces Wa and Wb have a conical shape as shown in the figure, and the both conical surfaces Wa and Wb are subjected to high-precision grinding. In addition to the demands, it is necessary to secure mass productivity as a machine element at the same time.However, there is no grinding technology that can satisfy both of these conditions, and mass production of inexpensive and highly accurate double tapered roller W is not possible. It was possible.

The present invention has been made in view of such conventional problems, and has as its object the use of a double-sided surface grinding technique having high processing accuracy and high processing efficiency, thereby making it inexpensive. An object of the present invention is to provide a grinding method and a grinding device capable of manufacturing a highly accurate double tapered roller.

[0012]

In order to achieve the above-mentioned object, a method for grinding a double tapered roller of the present invention is a grinding method using a double-headed surface grinding device of a feed-through grinding method, wherein the double tapered roller rotates on its own axis. While being held by the carrier as possible, by passing through between the grinding wheel surfaces of a pair of grinding wheels that are opposed and rotate in the opposite direction, the two conical surfaces of the both conical rollers contact the grinding wheel surface of the grinding wheel, respectively. The two conical surfaces are simultaneously ground while rotating the conical rollers.

As a preferred embodiment, the track for feeding through both conical rollers corresponds to the rotation direction of the two grinding wheels,
The rotation speed of the both tapered rollers is set to be constant or change continuously.

The double tapered roller grinding apparatus according to the present invention comprises:
A surface grinding method of a feed-through grinding method in which a carrier holding both conical rollers is allowed to pass between the grinding wheel surfaces of a pair of grinding wheels provided opposite to each other so as to preferably carry out the grinding method. In the apparatus, the pair of grinding wheels are arranged so that their grinding wheel surfaces are opposed to each other in parallel, and are configured to be driven to rotate in opposite directions to each other, and the carrier holds the two tapered rollers so that they can rotate. At least one carrier pocket is provided, and the carrier pocket is provided with a holding structure for holding the both conical rollers in a posture such that both conical surfaces are parallel to the grinding wheel surface of the grinding wheel.

Here, the double tapered roller means a conical body having a pair of conical outer peripheral surfaces which are coaxially aligned and whose bottoms are joined to each other.

In the present invention, the double tapered rollers are fed through a pair of grinding wheels, which are oppositely rotated in opposite directions, while being held by the carrier in a rotatable state. At this time, the two conical rollers, while passing between the two grinding wheels, the two conical surfaces are respectively contacted with the grinding wheel surfaces of the two grinding wheels, and as a result, the two rotating wheels are given a rotation force by the two grinding wheels and rotate. Simultaneous grinding by the grinding wheel surface is performed on both conical surfaces.

In the double-headed surface grinding of the feed-through grinding method, a large number of double-cone rollers can be mass-produced continuously and automatically in order to grind a work with one pass and high machining accuracy. Significant cost reduction is realized.

[0018]

Embodiments of the present invention will be described below with reference to the drawings.

Embodiment 1 FIG. 1 to FIG. 3 show a grinding apparatus according to the present invention. Specifically, this grinding apparatus is designed to have a double conical surface Wa, Wb of a double conical roller (work) W as shown in FIG. This is a vertical double-sided surface grinding machine for simultaneously grinding by a feed-through grinding method (through-grinding method), and is mainly composed of a pair of upper and lower grinding wheels 1, 2 and a carrier 3.

The grinding wheels 1 and 2 are so-called cup-shaped grinding wheels. The grinding wheels 1a and 2a at their end surfaces are flat annular grinding surfaces, and are arranged so as to be opposed to and parallel to each other. I have. Peripheral devices for rotating these grinding wheels 1 and 2 have a conventionally well-known structure. Wheels 1,
The two main shafts (grinding wheel shafts) 5 and 6 are rotatably supported on coaxial vertical lines, respectively, and are driving sources via a power transmission mechanism such as a transmission belt mechanism or a gear mechanism (not shown). Each is connected to a spindle motor. As will be described later, the two grinding wheels 1 and 2 are configured to be rotationally driven in directions opposite to each other (arrows a and b) in order to impart rotation to the work W. The rotational speeds (peripheral speeds) of the grinding wheels 1 and 2 are also appropriately set in consideration of the rotational speed required for the work W and the shape and dimensions of the work W and the carrier pocket 10 described later. .

The carrier 3 holds the workpiece W and feeds the workpiece W between the upper and lower grinding wheels 1 and 2 in the direction of the arrow c. ing. The peripheral device for rotating the carrier 3 has a conventionally well-known structure. As shown in FIG. 2, the carrier shaft 7 of the carrier 3 is rotatably supported in a vertical state similarly to the main shafts 5 and 6 of the grinding wheels 1 and 2 and a transmission belt mechanism (not shown). Through a power transmission mechanism described above.

The carrier 3 is in the form of a flat rotating disk that can be inserted and passed between the grinding wheel surfaces 1a and 2a of the grinding wheels 1 and 2 and, as shown in FIG. Carrier pockets 10 holding W are arranged at a plurality of locations (eight locations in the illustrated example) at equal intervals in the circumferential direction.

The carrier pocket 10 is formed in the form of a through-hole penetrating the carrier disk 3 up and down.
Are stored so as to be freely rotatable, and both conical surfaces Wa and Wb are configured to protrude from upper and lower surfaces 3 a and 3 b of the carrier disk 3.

Specifically, in the holding structure of the carrier pocket 10, the upper and lower ridge lines of the conical surfaces Wa and Wb of the work W are parallel to the grinding wheel surfaces 1a and 2a of the grinding wheels 1 and 2 (FIG. 3). (See (b))). In the state where the work W is stored and held in the carrier pocket 10, the axis XW of the work _W is shown in FIG.
in a plan view (a), the is configured to tilt at a predetermined plane inclination angle α with respect to the diameter line X _C of the carrier disc 3 passes approximately through the center of the workpiece W. In other words, when the work W is located on a straight line (= diameter line X _C ) connecting the rotation center of the carrier disk 3 and the rotation centers of the grinding wheels 1 and 2, the work W It is arranged with the inclination angle α.

In the case shown in the figure, the carrier pocket 10 is formed in the form of a substantially elliptical through hole vertically penetrating vertically, and the elliptical contour is, as shown in the figure, the outer peripheral contour of the work W stored and held therein. The contour shape is similar to. The planar inclination angle α of the axis X _W of the workpiece W which is housed and held in the carrier pocket 10 of the carrier disc 3 with respect to the diameter line X _C is set to correspond to the geometry of the workpiece W to 45 ° . Incidentally, in the double tapered roller as the work W, the angle formed by the upper and lower vertices, that is, the cone angle θ is 90 ° in the front shape shown in FIG. 4 (a), so that the intersection angle of both the conical surfaces Wa and Wb is also 90 °. Is set to

In order to ensure a high processing accuracy of the work W, the work W is controlled by the upper and lower grinding wheels 1 and 2 at a stable speed without rotation unevenness, that is, at a constant speed or a speed that changes continuously. It is necessary to rotate. In other words, as shown, the carrier disk 3
In the through grinding method by the rotation of the wheels, the grinding wheels 1, 2
Where the workpiece W passes in a circular orbit with respect to the rotation directions a and b of the grinding stone surfaces 1a and 2a (arrow c).
Direction), by setting the planar inclination angle α in the above conditions, the axis X _W of the workpiece W is not constant and gradually changes with respect to the grinding wheel surface 1a, the rotational direction of 2a of the grinding wheel 2 Nevertheless, the rotational force of the grinding wheels 1 and 2
This is because it has been experimentally found that the work W is always transmitted stably and the work W rotates at a stable rotation speed without rotation unevenness.

A work guide 15 as shown in FIG. 2 is provided below the carrier disk 3 corresponding to the holding structure of the carrier pocket 10. The work guide 15 cooperates with the carrier pocket 10 to guide the work W in the above-described posture.
Although not shown, the guide surface 15a is provided so as to extend in a fan shape or an arc shape corresponding to the movement locus of the carrier pocket 10. Specifically, in FIG. A is continuous from A to the insertion side of the grinding wheel surface 2a of the lower grinding wheel 2, and extends from the discharge side of the grinding wheel surface 2a to the workpiece discharge position B.

In the double-headed surface grinding apparatus constructed as described above, the workpieces (double conical rollers) W, W which are sequentially loaded into the carrier pockets 10, 10,... Are fed through the grinding wheel surfaces 1a and 2a of the upper and lower grinding wheels 1 and 2 which rotate in opposite directions with the rotation of the carrier disk 3, and are subjected to grinding. The paper is discharged from the carrier pocket 10 at the discharge position B.

In this case, the work W stored and held in the carrier pocket 10 so as to be freely rotatable, as described above,
The upper and lower ridges of the two conical surfaces Wa and Wb correspond to the two whetstone surfaces 1.
a, (see FIG. 3 (b)) with a parallel respectively 2a, that (in the illustrated 45 °) predetermined plane inclination angle α relative to the axis X _W is diameter line X _C of the carrier disc 3 with It is positioned so as to be inclined (see FIG. 3 (a)).

Therefore, the workpiece W sent between the grinding wheel surfaces 1a and 2a in this holding state is
a and 2a, the upper and lower grindstone surfaces 1a and 2a of which both conical surfaces Wa and Wb rotate in the reverse direction (arrows a and b directions) when passing between the a
As a result, the workpiece W is rotated by the rotational force of the grindstone surfaces 1a and 2a, and rotates at a stable speed without rotation unevenness in the carrier pocket 10 while maintaining the same posture. Grinding stone surface 1 on conical surfaces Wa and Wb
Simultaneous grinding by a and 2a is performed. Thereby, as shown in FIG. 4, the double conical roller W having the uniform conical surfaces Wa and Wb in which the upper and lower conical angles θ are 90 ° is manufactured.

In the double-headed surface grinding of such a through grinding method, the double conical rollers W are ground with one pass and with high machining accuracy, and a large number of double conical rollers W, W,. Can be mass-produced. As a result, the double tapered roller W, which has been impossible in the past,
, A large reduction in manufacturing cost can be realized.

The double tapered roller W thus manufactured
Is preferably applied as a component for a thrust force support structure in a scroll type compressor as shown in FIG. 5 (a), for example, and the outer peripheral surfaces Wa and Wb of the double tapered roller W are formed as shown in FIG.
As shown in (b), the rolling motion is performed in line contact with the flat bottom surfaces m and n of the concave portions h and i. As a result,
Compared to the conventional scroll type compressor using a rolling element consisting of a sphere for the above-mentioned support structure, the durability is remarkably improved, and furthermore, the characteristics by the scroll drive (less torque fluctuation and vibration, high speed operation is possible) It is possible to put a scroll-type compression machine that can be used without difficulty to practical use.

Embodiment 2 This embodiment is shown in FIG. 6, in which the shape and size of the carrier pocket 10 can be changed according to the standard size of the work W to be processed.

That is, the work holding jig 20 having the carrier pocket 10 is configured to be detachably mounted on the mounting portion 21 provided on the carrier disk 3.

The work holding jig 20 is a block having a cylindrical outer peripheral surface, and has an upper large diameter portion 20a and a lower small diameter portion 2a.
0b, the outer peripheral boundary portion 20c is a locking step portion, and the carrier pocket 10 is provided in the center portion so as to penetrate vertically. On the other hand, the mounting portion 21 is in the form of a fitting hole having a cylindrical inner surface corresponding to the cylindrical outer peripheral surface of the work holding jig 20, and has a locking shoulder 21a that engages with the locking step 20c. doing.

Further, at a position on one diameter line of the work holding jig 20 as viewed in a plane, a screw portion 23 for a tightening screw 22 is provided at the boundary between the work holding jig 20 and the mounting portion 21. Is provided in correspondence with. Then, in a state where the work holding jig 20 is placed and fitted on the mounting portion 21 from above, the work holding jig 20 is tightened by the tightening screws 22, 22, so that the carrier pocket 10
Are fixed so as to be positioned on the carrier disk 3 with the above-mentioned plane inclination angle α.

With such a configuration, it is possible to selectively use the carrier pocket 10 having a shape and size corresponding to various standard dimensions of the work W to be machined, and to wear the carrier pocket 10. It is possible to perform an exchange operation appropriately corresponding to the above. In addition, the work holding jig 20 can be made of a material different from that of the carrier plate 3, and an optimum material for the carrier pocket 10 can be adopted. Other configurations and operations are the same as those of the first embodiment.

Embodiment 3 This embodiment is shown in FIG. 7, and is a further modification of Embodiment 2, in which the mounting posture of the work W on the carrier disk 3 can be adjusted.

That is, the work holding jig 25 having the carrier pocket 10 is configured to be removably mounted on the mounting portion 26 provided on the carrier disk 3, and is mounted on the mounting portion 26. , The plane inclination angle α of the carrier pocket 10 can be adjusted.

The work holding jig 25 is a block-shaped member having a cylindrical outer peripheral surface, as in the second embodiment, and includes an upper large-diameter portion 25a and a lower small-diameter portion 25b. The mounting portion 26 is a stepped portion.
The fitting step has a cylindrical inner surface corresponding to the cylindrical outer peripheral surface of the work holding jig 25.
c has a locking shoulder 26a.

The upper large-diameter portion 25a of the work holding jig 25 is structured to be rotatably fitted to the inner diameter surface of the mounting portion 26. Each of the adjusting long holes 28 that can penetrate the screw portion and engage with the head is provided. And
In a state where the work holding jig 25 is placed and fitted on the mounting portion 26 from the upper side, the position in the rotation direction is adjusted, and then the tightening screws 27, 27 are tightened. Is fixed so as to be positioned on the carrier disk 3 with the above-mentioned plane inclination angle α.

With such a configuration, in addition to the same effects as in the above-described second embodiment, the carrier can be held so that the workpiece W is held at an optimal plane inclination angle α for its rotation action. The position of the pocket 10 can be adjusted appropriately. Other configurations and operations are the same as those of the first embodiment.

Embodiment 4 This embodiment is shown in FIG.
Ten holding structures were modified.

That is, the carrier pocket 110 has a planar rectangular shape as shown in the figure, and is in the form of a through hole vertically penetrating the carrier disk 3.

The specific holding structure of the carrier pocket 110 is the same as in the first embodiment, except that the upper and lower ridges of the conical surfaces Wa and Wb of the work W are
a, while being configured to maintain the posture in parallel, respectively (see FIG. 8 (b)) to the 2a, the axis X _W of the workpiece W to be housed and held here, as shown in Figure 8 (a) , The carrier disk 3 passing through the center of the workpiece W
It is configured so as to be inclined at a predetermined plane inclination angle α with respect to the diameter line X _C.

To this end, as shown, a pair of opposing sides 110a, 110 of the carrier pocket 110 are shown.
b is an inclined flat surface, and in the illustrated case, the inclination angle β of the carrier disk 3 with respect to the upper and lower surfaces 3a, 3b is 45 ° corresponding to the shape and size of the workpiece W, similarly to the above-mentioned plane inclination angle α. Is set.

Thus, with such a configuration, when the work W stored and held in the carrier pocket 110 passes between the grinding wheel surfaces 1a and 2a of the upper and lower grinding wheels 1 and 2, these grinding wheel surfaces are used. The two conical surfaces Wa and Wb are simultaneously ground while being rotated at a stable speed without rotation unevenness by being given a rotation force by the rotation forces 1a and 2a. Other configurations and operations are the same as those of the first embodiment.

The above-described first to fourth embodiments merely show preferred embodiments of the present invention, and the present invention is not limited to these embodiments, and various design changes can be made within the scope. .

For example, in the illustrated embodiment, the carrier 3 for sending the double tapered rollers W is in the form of a rotating disk that makes a rotational movement, and the through feed track is a circular track. Alternatively, it may be in the form of a reciprocating angular table, and the feed-through trajectory may be a linear trajectory.
In short, as long as the trajectory to be fed through the double conical rollers W can be set so that the rotation speed of the double conical rollers W is constant or continuously changed in accordance with the rotation direction of the upper and lower grinding wheels 1 and 2. It is also possible to adopt a through-feed configuration other than that illustrated.

The specific form (planar shape and cross-sectional shape) of the carrier pockets 10 and 110 is determined in consideration of the rotation speed required for the double tapered roller W to be machined and the shape and size of the double tapered roller W and the grinding wheel. It is set appropriately in accordance with the rotational speeds of the cars 1 and 2, and is not necessarily limited to the illustrated form.

The illustrated double-cone roller W has a geometrically perfect double-cone shape consisting of only a pair of conical members. The present invention can also be applied to those having a substantially biconical shape, such as a slight cylindrical portion or the like intervening in the joint portion between the bottom portions, or having a rounded top portion of the upper and lower cones. is there.

Further, in the illustrated embodiment, a case is shown in which the main spindles 5 and 6 of the grinding wheels 1 and 2 are arranged vertically in a vertical double-sided surface grinding machine.
Can also be applied to a horizontal-axis double-ended surface grinding machine in which is disposed horizontally.

[0053]

As described above in detail, according to the grinding method of the present invention, while the double tapered rollers are held by the carrier in a rotatable state, they are passed between a pair of grinding wheels that rotate in opposite directions. By contacting the conical surfaces of the conical rollers with the grindstone surface of the grinding wheel, and simultaneously grinding the conical surfaces while rotating the conical rollers, inexpensive and highly accurate It is possible to manufacture double tapered rollers.

In other words, high-precision grinding is required for the upper and lower conical surfaces of the double conical rollers, and the double-sided surface grinding technique of the feed-through grinding method can be used for this grinding, which results in high machining. Grinding with high accuracy and high processing efficiency is realized, and a large number of double tapered rollers can be mass-produced continuously and automatically. As a result, a large reduction in the manufacturing cost can be realized by a large amount of processing of the double tapered roller, which has been impossible in the past.

Therefore, a thrust force support structure having the double tapered rollers as a component, and a scroll type compressor having this support structure and having much improved durability as compared with the prior art, can be put to practical use. became.

The grinding apparatus of the present invention can be constructed by slightly modifying a general double-sided surface grinding machine. For example, the above-mentioned existing double-sided surface grinding machine can be easily used. The grinding method can be performed, and the cost of the apparatus can be reduced.

[Brief description of the drawings]

FIG. 1 is a plan view showing a schematic configuration of a double tapered roller grinding device according to a first embodiment of the present invention.

FIG. 2 is a front view showing a schematic configuration of the grinding device in a partial cross section.

FIG. 3 is an enlarged view showing a main part of the grinding apparatus, FIG. 3 (a) is an enlarged plan view excluding an upper grinding wheel, and FIG. 3 (b) is FIG.
FIG. 3A is a cross-sectional view along the line III-III.

4 (a) is a front view and FIG. 4 (b) is a plan view showing a double conical roller to be ground by the grinding apparatus.

FIG. 5 (a) is a schematic cross-sectional view of a scroll type compressor having a thrust force support structure using double tapered rollers, and FIG. 5 (b) shows a rolling motion state of the double tapered rollers. It is a schematic diagram for description.

FIG. 6 is an enlarged view showing a main part of a grinding device according to a second embodiment of the present invention, FIG. 6 (a) is an enlarged plan view excluding an upper grinding wheel, and FIG. 6 (b) is a double tapered roller. VI of Fig. 6 (a) excluding
FIG. 6 is a sectional view taken along the line -VI.

FIG. 7 is an enlarged view showing a main part of a grinding device according to a third embodiment of the present invention, FIG. 7 (a) is an enlarged plan view excluding an upper grinding wheel, and FIG. 7 (b) is a double tapered roller. VI of Fig. 7 (a) excluding
FIG. 6 is a sectional view taken along the line -VI.

FIG. 8 is an enlarged view showing a main part of a grinding device according to a fourth embodiment of the present invention, FIG. 8 (a) is an enlarged plan view excluding an upper grinding wheel, and FIG. 8 (b) is FIG. () Is a cross-sectional view along the line VI-VI.

[Explanation of symbols]

X _W Axis of double tapered roller X _C Diameter line of carrier disk α Flat tilt angle of double tapered roller β Tilt angle of side of carrier pocket θ Conical angle of double tapered roller W Double tapered roller Wa, Wb Conical surface of double tapered roller 1, 2 grinding wheels 1a, 2a grinding wheel surface of grinding wheel 3 carrier disk (carrier) 3a, 3b upper and lower surfaces of carrier disk 5, 6 spindle of grinding wheel 7 spindle of carrier disk 10 carrier pocket 15 work guide 20 work Holding jig 25 Work holding jig 110 Carrier pocket 110a, 110b Side face of carrier pocket

Claims (7)

[Claims] 1. A grinding method using a double-headed surface grinding device of a feed-through grinding method, wherein a double-cone roller is held on a carrier in a rotatable manner,
The two conical rollers are brought into contact with the grindstone surfaces of the grinding wheels, respectively, by being fed between the grinding wheel surfaces of a pair of grinding wheels that are oppositely rotated in the opposite direction. A double-cone roller grinding method characterized in that conical surfaces are simultaneously ground. 2. The trajectory for feeding through both conical rollers is set such that the rotation speed of the conical rollers changes constantly or continuously in accordance with the rotation direction of the two grinding wheels. The method for grinding a double tapered roller according to claim 1. 3. A double-end surface grinding apparatus of a feed-through grinding type wherein a carrier holding a pair of conical rollers can pass between the grinding wheel surfaces of a pair of grinding wheels provided to face each other. The grinding wheels are arranged so that their grinding surfaces face in parallel, and are configured to be driven to rotate in opposite directions to each other. The carrier has at least one carrier pocket that holds both conical rollers in a rotatable manner. The grinding machine for double tapered rollers, characterized in that the carrier pocket has a holding structure for holding the attitude of the double tapered rollers such that both the conical surfaces thereof are parallel to the grinding wheel surface of the grinding wheel. 4. The carrier is in the form of a rotating disk having at least one carrier pocket that holds both conical rollers in a rotatable manner. The holding structure of the carrier pocket includes 4. The grinding device for double tapered rollers according to claim 3, wherein the axis is configured to be inclined with respect to a diameter line of the carrier passing substantially in the center of the double tapered rollers when viewed in a plane. 5. The carrier pocket according to claim 4, wherein the carrier pocket has a substantially elliptical planar shape, and has a contour shape similar to the outer peripheral contour of the double tapered roller holding the elliptical contour. A grinding device for double tapered rollers according to item 1. 6. The double tapered roller grinding apparatus according to claim 3, wherein the work holding jig having the carrier pocket is detachably mounted on the carrier. . 7. The double tapered roller grinding apparatus according to claim 3, wherein the work holding jig is capable of adjusting a mounting posture of the work holding jig.