JP2013094945A - Grinding liquid supply structure for two-way action coolant nozzle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a grinding liquid supply structure for a two-way action coolant nozzle that can supply a grinding liquid and a coolant in two ways by a simple configuration, and is inexpensive.SOLUTION: A semispherical or spherical fixed shaft projection 11 is formed at a part of a fixed shaft 10 in which a flow passage for supplying the grinding liquid is formed, and the fixed shaft projection has a communication hole for feeding the grinding liquid to a rotatable nozzle body 50. A nozzle base 53 of the nozzle body which is formed in a funnel shape is arranged opposite to the fixed shaft projection. While the fixed shaft projection is fixed, the nozzle base is rotatable around a nozzle axis, and movable along a peripheral surface of the fixed shaft projection, and the fixed shaft projection and nozzle base are sealed with an elastic seal member. The grinding liquid is fed in a liquid-tight state from the fixed shaft to a nozzle tip 51 through the elastic seal member 80 without reference to relative positions of the fixed shaft projection part and nozzle base.

Description

  The present invention relates to a structure for supplying a grinding fluid to a two-way operation coolant nozzle that can be suitably used when, for example, a grinding fluid or a coolant is supplied to a workpiece or a tool during operation of a machine tool.

  For example, a structure is known in which grinding fluid or coolant fluid is supplied to a workpiece or tool during operation of a machine tool (see Patent Document 1). This grinding liquid supply structure has an injection hole for injecting the grinding liquid and an injection piece for changing the direction of the injection hole to supply the grinding liquid.

JP 7-266105 A

  In the above-described grinding fluid supply structure, the grinding fluid spraying direction can be changed by adjusting the direction of the spraying piece. However, when adjusting the injection direction, the supply of the grinding fluid must be temporarily stopped due to its structure. Therefore, it is not possible to freely adjust the injection direction while supplying the grinding fluid.

  Therefore, although not yet known at the time of filing of the present invention, a grinding fluid supply structure 100 related to the present invention as shown in FIGS. 5 and 6 can be considered. Here, FIG. 5 is a front view showing a structure for supplying a grinding fluid to the two-way operation coolant nozzle related to the present invention. FIG. 6 is an explanatory diagram for partially explaining the structure for supplying the grinding fluid to the two-way operation coolant nozzle shown in FIG. The structure for supplying the grinding fluid includes a nozzle 150 for injecting the grinding fluid, a so-called oil lead 190 that allows the nozzle 150 to rotate in two axial directions and guides the supplied grinding fluid to the nozzle 150, and the grinding fluid to the oil lead 190. A shaft 110 having a flow path 110a to be fed to, three bevel gears 131, 132, 133 (130), a first motor 121 (120) and a second motor for driving the first to third bevel gears 130 122 (120), a power transmission gear 125 provided in each motor 120, a power transmission gear 126 provided integrally with the first bevel gear 131 and the second bevel gear 132, and a bracket 140 for supporting them.

  As shown in FIG. 5, the grinding fluid passes from the grinding fluid supply hose (not shown) through the flow path 110a inside the shaft, and passes through the opening 111 of the shaft 110, the oil lead internal space 190a, and the communication hole 190b (see FIG. 6). Thus, it is supplied to the nozzle 150.

  The tip of the nozzle 150 rotates in the left-right direction in FIG. 5 or in the up-down direction depending on the combination of the rotation directions of the bevel gear 130 that is rotated by driving the motor 120. The grinding fluid supply structure related to the present invention having such a configuration can freely adjust the injection direction of the grinding fluid by the nozzle even when the grinding fluid is being supplied.

  However, in order to supply the grinding fluid while enabling two-way operation, a complicatedly shaped nozzle 150 and oil lead 190 are required. Moreover, it is necessary to interpose the seal member 180 at three places in total, and the replacement work accompanying the deterioration of the seal member 180 becomes complicated. Moreover, since the number of parts increases, cost reduction cannot be achieved.

  An object of the present invention is to provide a grinding fluid supply structure for a two-way operation coolant nozzle that can supply grinding fluid and coolant in two directions (biaxial directions) with a simple configuration and is inexpensive.

In order to solve the above-described problem, a structure for supplying a grinding fluid to a bidirectional operation coolant nozzle according to claim 1 of the present invention includes:
In a two-way operation coolant nozzle that supplies grinding fluid or coolant fluid to workpieces and tools of machine tools,
A hemispherical or spherical fixed shaft protrusion is provided on a part of the fixed shaft in which the flow path for supplying the grinding liquid is formed,
The fixed shaft protrusion includes a communication hole for feeding the grinding liquid to the rotatable nozzle body,
The nozzle base formed in the funnel shape of the nozzle body is disposed to face the fixed shaft protruding portion, and the nozzle base can rotate around the nozzle axis while the fixed shaft protrusion is fixed. And is movable along the peripheral surface of the fixed shaft protrusion,
Between the fixed shaft protrusion and the nozzle base is sealed by an elastic seal member,
Regardless of the relative position of the fixed shaft protrusion and the nozzle base, the grinding fluid is fed in a liquid-tight manner from the fixed shaft to the tip of the nozzle through the seal member.

  Since the structure for supplying the grinding fluid to the two-way operation coolant nozzle according to claim 1 has such a configuration, the grinding fluid is always changed to the optimum direction with respect to the workpieces and tools having various forms. Can be continuously supplied at a stable flow rate.

  Moreover, the complicated shape nozzle and oil lead in the structure for supplying the grinding fluid to the two-way operation coolant nozzle related to the present invention as shown in FIGS. 5 and 6 are not required. In addition, since there is no need to provide the seal member at three places as in the related invention, only one place is sufficient, so that the labor of replacement work accompanying the deterioration of the seal member can be reduced. And the number of parts can be reduced, which contributes to cost reduction. Further, the outer diameter around the rotation axis of the nozzle body can be reduced as compared with the related invention. Therefore, the rotational torque for quickly moving the nozzles is small, and the motor can be miniaturized.

Moreover, the grinding fluid supply structure to the two-way operation coolant nozzle according to claim 2 of the present invention is the grinding fluid supply structure to the two-way operation coolant nozzle according to claim 1,
An engagement groove for holding the elastic seal member is formed in the nozzle base portion or the fixed shaft protruding portion.

  The grinding fluid supply structure to the two-way operation coolant nozzle according to claim 2 has such a configuration, so that the engagement groove for attaching the elastic seal member can be attached to either the nozzle base portion or the fixed shaft protruding portion. The elastic seal member can be firmly fitted into the engagement groove of the nozzle base or the fixed shaft protrusion. As a result, even if the bi-directional coolant nozzle is used over a long period of time, the elastic seal member does not shift with respect to the nozzle base portion and the fixed shaft protruding portion to which the elastic seal member is fitted. Leakage can be prevented.

Moreover, the grinding fluid supply structure to the two-way operation coolant nozzle according to claim 3 of the present invention is the grinding fluid supply structure to the two-way operation coolant nozzle according to claim 1,
The virtual curved surface formed by the movement trajectory of the elastic seal member provided in the nozzle base is made to correspond to the curved surface of the surface of the fixed shaft protruding portion along which the elastic seal member extends.

  The structure for supplying the grinding fluid to the two-way operation coolant nozzle according to claim 3 has such a configuration, more specifically, the elastic seal member follows a virtual curved surface formed by the movement locus of the elastic seal member provided in the nozzle base. By matching the radius of curvature (1 / curvature) with the curved surface of the surface of the fixed shaft projection, the nozzle tip is moving, that is, the nozzle base is on the peripheral surface of the fixed shaft projection. Since the elastic seal member is extremely compressed along the predetermined distance, the elastic seal member is extremely compressed and broken, or the gap between the nozzle base and the fixed shaft protruding portion becomes large and the sealing performance of the elastic seal member is impaired. There is nothing. In addition, the nozzle can be easily rotated, and the rotation speed of the nozzle can be increased, so that the grinding liquid can be supplied to a desired portion with good responsiveness.

  ADVANTAGE OF THE INVENTION According to this invention, the grinding fluid supply structure to a two-way operation | movement coolant nozzle which can supply a grinding fluid and a coolant in two directions (biaxial direction) with a simple structure and is inexpensive can be provided.

It is a front view which shows the grinding fluid supply structure to the two-way action | operation coolant nozzle which concerns on one Embodiment of this invention. FIG. 2 is a cross-sectional view for explaining the operation of the coolant nozzle bi-directional operation structure shown in FIG. 1, showing a state in which the nozzle body is positioned on the upper side in the drawing and the nozzle tip is directed obliquely upward to the left in the drawing ( FIG. 2 (a)) and a sectional view (FIG. 2 (b)) showing a state in which the nozzle body is positioned on the upper side in the drawing and the tip of the nozzle is directed obliquely upward to the right in the drawing. FIG. 2 is a cross-sectional view for explaining the operation of the coolant nozzle bi-directional operation structure shown in FIG. 1, and is a cross-sectional view showing a state in which the nozzle body is rotated to the upper right and the nozzle tip is directed upward in the drawing. FIG. 3 (a)) and a sectional view (FIG. 3 (b)) showing a state in which the nozzle body is rotated obliquely upward to the left in the drawing and the nozzle tip is directed to the left in the drawing. It is a front view which shows the modification of the grinding fluid supply structure to the two-way action | operation coolant nozzle which concerns on this embodiment. It is a front view which shows the grinding fluid supply structure to the two-way action | operation coolant nozzle relevant to this invention. It is explanatory drawing which expands and demonstrates partially the grinding fluid supply structure to the two-way operation | movement coolant nozzle shown in FIG.

  Hereinafter, a structure for supplying a grinding fluid to a two-way operation coolant nozzle according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a front view showing a structure for supplying a grinding fluid to a two-way operation coolant nozzle according to the present embodiment.

  The grinding fluid supply structure to the two-way operation coolant nozzle according to the embodiment of the present invention supplies a grinding fluid or a coolant fluid (hereinafter referred to as “grinding fluid”) to a workpiece or a tool during operation of a machine tool, for example. The first to third bevel gears 31, 32, 33 (30) disposed inside the bracket 40 and the bracket 40 that holds the first to third bevel gears 30. A fixed shaft 10 disposed through the first bevel gear 31 and the second bevel gear 32 in a common axial direction of these gears, a fixed shaft support frame 70 for fixing the fixed shaft 10, and a third bevel gear. The first motor 21 (20) and the second motor 22 (20) that respectively drive the nozzle body 50 projecting in the direction of the central axis 33 and the first to third bevel gears 30. If, a power transmission gear 25 provided in each motor 20, and a power transmission gear 26 provided integrally with the first bevel gear 31 and a second bevel gear 32.

  The fixed shaft 10 has a spherical fixed shaft protruding portion 11 at the center portion in the longitudinal direction of the fixed shaft. The fixed shaft 10 has a hose connecting portion 60 at one end (right side in FIG. 1), and a hose (not shown here) for supplying a grinding fluid from a grinding fluid supply source (not shown) to the grinding fluid supply path 10a. ) Is connected to the hose connection 60. Both ends of the fixed shaft 10 are supported via a fixed shaft support frame 70 so that the fixed shaft itself does not rotate.

  The grinding fluid supply path 10a is formed inside the fixed shaft, extends from one end (right side in FIG. 1) of the fixed shaft 10 to the fixed shaft protruding portion 11, and is orthogonal to the extended end portion on the surface of the fixed shaft. It extends to the formed protrusion 11a for supplying the grinding fluid. That is, a grinding fluid supply path is formed from one end (right side in FIG. 1) of the fixed shaft 10 to the projecting portion side opening 11 a of the fixed shaft projecting portion 11, and serves as a communication hole for supplying the grinding fluid to the nozzle base 53. Yes.

  The nozzle body 50 is formed from a nozzle tip 51, a nozzle shaft 52, and a nozzle base 53. The nozzle body has a grinding liquid supply path 50 a for supplying the grinding liquid to the nozzle tip 51. The nozzle base 53 has a funnel shape, and a flange 53b is formed on the entire periphery of the edge of the enlarged opening.

  The flange 53b moves along a spherical surface of the fixed shaft projecting portion 11 with a certain slight interval while sandwiching an O-ring (elastic seal member) 80 (see FIGS. 2 and 3). At the same time, it rotates around the central axis of the nozzle shaft 52. The shape of the flange 53 b is a shape corresponding to the curved surface shape of the fixed shaft protruding portion 11. That is, the curvature radius (1 / curvature) of the virtual curved surface formed by the movement trajectory of the O-ring 80 provided in the nozzle base 53 substantially matches the curved surface of the surface of the fixed shaft protruding portion 11 along which the O-ring 80 extends. It corresponds to. Further, an engaging groove 53c (see FIG. 2) is formed on the flange 53b on the surface facing the fixed shaft protruding portion 11 over the entire circumference. The O-ring 80 is fitted into the engagement groove 53 c so as to be in pressure contact with the contact surface of the fixed shaft protruding portion 11, and the nozzle base portion 53 is projected from the protruding portion side opening 11 a formed in the fixed shaft protruding portion 11. Sealing is performed via an O-ring 80 so that the grinding fluid flowing through the nozzle-side inflow hole 53a formed in is not leaked to the outside.

  The sealing means used in the present invention is not limited to the O-ring 80 as in the present embodiment, and any elastic sealing member that is firmly in pressure contact with the fixed shaft protruding portion 11 may be used. That is, for example, an elastic seal member having a contact surface having a fillet shape may be used.

  Next, the configuration of the bevel gear 30 will be described. The first bevel gear 31 and the second bevel gear 32 have the same pitch and the same number of teeth, and are arranged on the same rotational axis at a predetermined interval so that the gears face each other. The third bevel gear 33 meshes with both the first bevel gear 31 and the second bevel gear 32. The third bevel gear 33 is disposed between the first bevel gear 31 and the second bevel gear 32 so that the axis thereof is orthogonal to the axes of the first bevel gear 31 and the second bevel gear 32. In the case of the present embodiment, the number of teeth and the pitch of the third bevel gear 33 are the same as the number of teeth and the pitch of the first and second bevel gears 31 and 32. Accordingly, in the present embodiment, the gear ratio between the third bevel gear 33 and the first bevel gear 31 and the gear ratio between the third bevel gear 33 and the second bevel gear 32 are 1.

  In the present embodiment, a power transmission gear 25 is fixed to the tip of the output shaft of each of the first motor 21 (20) and the second motor 22 (20), and the motor 20 is driven to drive the power transmission gear 25. Correspondingly, the first to third bevel gears 30 (31, 32, 33) rotate correspondingly via the power rotating gear 26 integrated with the first bevel gear 31 and the second bevel gear 32, respectively. It has become. In the present embodiment, stepping motors are used for the first motor 21 and the second motor 22. Note that the same stepping motor is used for the first motor 21 and the second motor 22.

  In the case of this embodiment, the bracket 40 has a shape obtained by bending an elongated metal plate into a square U-shape when viewed from the front in FIG. The first bent portion 41 and the first bevel gear 31 of the bracket 40 are formed with insertion holes 41 a and 31 a for inserting the fixed shaft protruding portion 11.

  Similarly, the second bent portion 42 and the second bevel gear 32 of the bracket 40 are formed with insertion holes 42a and 32a for inserting the fixed shaft. A cylindrical protrusion 45 is formed on the upper surface of the nozzle support part 43 sandwiched between the first bent part 41 and the second bent part 42 of the bracket 40. The axis of the cylindrical protrusion 45 coincides with the axis of the nozzle shaft 52. Further, the nozzle shaft insertion hole 45 a formed in the axial direction of the cylindrical projecting portion 45 is formed so as to penetrate the central portion of the bracket 40. The inner diameter of the nozzle shaft insertion hole 45a is slightly larger than the outer diameter of the nozzle shaft 52, and the nozzle shaft 52 is rotatably held by the protrusion 45.

  The protrusion 45 of the bracket 40 supports the nozzle shaft 52 and follows the movement of the nozzle shaft 52 around the axis of the first and second bevel gears 31 and 32 to move the bracket 40 to the first and second bevel gears 31. , 32 is moved with a locus on an arc around the axis of 32. As a result, the nozzle base 53 moves at a constant slight distance with the O-ring 80 sandwiched along the spherical outer peripheral surface of the fixed shaft protrusion 11.

  There is a certain gap between the outer peripheral surface of the fixed shaft 10 and the inner peripheral surface of the bracket 40 and the insertion hole 41a of the first and second bevel gears. In this embodiment, the bearings 91 and 92 can be rotated relative to each other. In addition, the bracket 40 and the first to third bevel gears 30 are supported by the fixed shaft 10 via the bearings 91 and 92. In place of the bearings 91 and 92, an O-ring may be provided in the gap of this portion.

  There is a certain gap between the third bevel gear 33 and the central portion of the bracket 40, and the meshing between the third bevel gear 33 and the first and second bevel gears 31, 32 is maintained and the third bevel gear is maintained. The third bevel gear 33 can rotate smoothly without the side surface opposite to the gear 33 interfering with the nozzle support portion 43 of the bracket 40.

  Next, a specific flow of the grinding fluid in the above-described two-way operation coolant nozzle will be described. The grinding fluid flows from a grinding fluid supply source to a hose (these are not shown here), and from the hose to the grinding fluid supply path 10a inside the fixed shaft. And it flows into the protrusion part side opening part 11a of the surface of the fixed shaft protrusion part 11 from the grinding fluid supply path 10a. Subsequently, it flows into the nozzle side inflow hole 53a through the nozzle base part from the protrusion part side opening part 11a. Next, it flows from the nozzle-side inflow hole 53a to the grinding fluid supply path 50a inside the nozzle body, is sprayed from the nozzle tip 51, and is supplied to the object to be ground.

  Subsequently, a specific operation of the grinding fluid supply structure 1 to the two-way operation coolant nozzle according to the present embodiment will be described. FIG. 2 is a front view for explaining the operation of the coolant nozzle bi-directional operation structure shown in FIG. 1, in which the nozzle body 50 is positioned on the upper side and the nozzle tip 51 is directed obliquely upward to the left in the drawing. The figure which shows a state (FIG.2 (a)), and the figure which shows the state (FIG.2 (b)) which has made the nozzle main body 50 located in the upper side in the figure, and made the nozzle front-end | tip 51 face the diagonally upper right in the figure. . FIG. 3 is a side view for explaining the operation of the coolant nozzle bi-directional operation structure shown in FIG. 1, in which the nozzle body 50 is rotated to the upper right side in the drawing and the nozzle tip 51 is directed upward in the drawing. The figure which shows the state (FIG.3 (a)) which made it show, and the figure which shows the state which rotated the nozzle main body 50 to the left diagonal upper direction in the figure, and made the nozzle tip 51 face the left side in the figure (FIG.3 (b)). It is. 2 and 3, illustration of the motor 20 and the power transmission gear 25 is omitted.

  For example, with reference to the state of FIG. 2A, the first bevel gear 31 rotates clockwise by a predetermined angular velocity by 180 ° when viewed from the gear side of the first bevel gear 31, and the second bevel gear 32 is When the second bevel gear 32 rotates 180 ° clockwise at the same predetermined angular velocity as that of the first motor 21 as viewed from the gear side, the third bevel gear 33 is viewed from the gear side of the third bevel gear 33. Rotate 180 ° counterclockwise. As described above, when the third bevel gear 33 is rotated by 180 °, the nozzle shaft 52 is also rotated accordingly, and the nozzle body 50 is moved from the state shown in FIG. 2A to the state shown in FIG. Change the direction. At this time, the nozzle base 53 also rotates at a constant interval while sandwiching the peripheral surface of the fixed shaft protrusion 11 and the O-ring 80. Here, the movable range of the nozzle base 53 is a range that does not exceed the protruding portion side opening 11 a of the fixed shaft protruding portion 11 even if the O-ring 80 engaged with the nozzle base 53 is movable. That is, the liquid is supplied from the protruding portion side opening 11 a of the fixed shaft protruding portion 11 to the nozzle body 50 while maintaining a liquid-tight state between the nozzle base portion 53 and the fixed shaft protruding portion 11 via the O-ring 80. It is designed to flow without leaking. For this reason, the grinding liquid is supplied to the nozzle tip 51 without leaking even when the nozzle tip 51 is moving.

  The first bevel gear 31 rotates 90 ° counterclockwise at a predetermined angular speed when viewed from the gear side, and the second bevel gear 32 rotates clockwise with the first motor 21 when viewed from the gear side. When rotating at the same predetermined angular velocity by 90 °, that is, the first bevel gear 31 and the second bevel gear 32 are rotated at the same angular velocity by 90 ° counterclockwise as viewed from the state of FIG. In this case, the third bevel gear 33 is rotated by an angle of 90 ° around the axis of the fixed shaft 10 from the gear side of the first bevel gear 31 without rotating in a state of meshing with the first and second bevel gears 31 and 32. Rotate. As described above, when the first bevel gear 31 and the second bevel gear 32 and the nozzle shaft 52 integrated with the first bevel gear 31 and the nozzle shaft 52 integrated with the first bevel gear 31 are rotated by 90 °, the movement of the nozzle shaft 52 causes the bracket 40 to rotate accordingly. As a result, the nozzle body 50 changes the direction of the nozzle tip 51 from the state shown in FIG. 3A to the state shown in FIG. At this time, the nozzle base 53 also rotates at a constant interval while firmly sandwiching the O-ring 80 along the peripheral surface of the fixed shaft protruding portion 11. Here, the movable range of the nozzle base 53 is a range that does not exceed the protruding portion side opening 11 a of the fixed shaft protruding portion 11 even if the O-ring 80 engaged with the nozzle base 53 is movable. That is, the liquid is supplied from the protruding portion side opening 11 a of the fixed shaft protruding portion 11 to the nozzle body 50 while maintaining a liquid-tight state between the nozzle base portion 53 and the fixed shaft protruding portion 11 via the O-ring 80. It is designed to flow without leaking. For this reason, the grinding liquid is supplied to the nozzle tip 51 without leaking even when the nozzle tip 51 is moving.

  Then, the effect | action of the grinding fluid supply structure to the two-way operation | movement coolant nozzle which concerns on one Embodiment of this invention is demonstrated. The coolant nozzle bi-directional operation structure according to the present embodiment has the above-described configuration, so that the flow rate of the grinding fluid can be stabilized while always changing the nozzle direction to the optimum direction for workpieces and tools having various forms. Can continue to supply. Further, since the grinding fluid supply path 10 a is formed in the fixed shaft 10, the hose connected thereto does not move as the nozzle body 50 moves.

  Further, unlike the related invention of the present invention as shown in FIGS. 4 and 5, there is no need for a complicatedly shaped nozzle or oil lead in the structure for supplying the grinding liquid to the two-way operation coolant nozzle. Further, unlike the related invention, there is no need to provide the seal member at three places, and only one place is sufficient. Therefore, the trouble of replacement work accompanying the deterioration of the seal member 180 can be reduced. And the number of parts of the oil lead 190 and the seal member 180 can be reduced, which contributes to cost reduction. Further, since the outer diameter around the rotation axis of the nozzle body 50 can be reduced as compared with the related invention, the rotational torque for quickly moving the nozzle body 50 can be reduced, and the motor 20 can be downsized.

  Further, since the O-ring 80 is firmly fitted in the engagement groove 53c of the nozzle base 53, the nozzle in which the O-ring 80 is fitted even if the bi-directional operation coolant nozzle is used for a long period of time. There is no deviation with respect to the base 53, and leakage of the grinding fluid from the O-ring 80 can be reliably prevented.

  Further, the virtual curved surface formed by the movement trajectory of the O-ring 80 provided in the nozzle base 53 is adapted so that the curvature radius (curvature) thereof substantially matches the curved surface of the surface of the fixed shaft protruding portion 11 along which the O-ring 80 extends. Therefore, during movement of the nozzle tip 51, that is, the nozzle base 53 always moves with a predetermined gap along the peripheral surface of the fixed shaft protruding portion 11, the O-ring 80 is extremely compressed and the O-ring is compressed. 80 is not broken, and the gap between the nozzle base 53 and the fixed shaft protrusion 11 is not increased and the sealing performance is not impaired. Further, the nozzle body 50 can be easily rotated, and the rotational speed of the nozzle body 50 can be increased to supply the grinding liquid to a desired location with good responsiveness.

  In the above-described embodiment, the engagement groove 53c is provided on the nozzle base side, and the seal member made of the O-ring 80 is fitted into the engagement groove. Without limitation, an engagement groove may be provided on the fixed shaft protruding portion side, and an O-ring or a fillet-shaped seal member may be fitted into the engagement groove.

  Further, the shape of the fixed shaft protruding portion 11 may be a curved surface only at a portion where the nozzle base 53 moves on the surface of the fixed shaft protruding portion 11. Therefore, although not shown here, unlike the present embodiment, the lower side 1/3 of the fixed shaft protrusion 11 in FIG. 1 may form a horizontal plane. In FIG. A so-called drum shape may be used in which both sides in the axial direction form a vertical plane outside the movable range of the O-ring 80 engaged with the nozzle base 53. This can reduce the material cost of the parts.

  The nozzle base 53 is not limited to the funnel shape, and the nozzle base passes from the protrusion side opening 11a of the fixed shaft protrusion 11 through the grinding liquid supply path 10a provided in the fixed shaft. Any shape such as a cup shape or a cross-sectional parabolic shape may be used as long as it flows through the nozzle side inflow hole 53a of the portion 53 without resistance.

  Further, in the above-described embodiment, the surface along which the O-ring 80 of the fixed shaft protrusion 11 and the engagement curved surface 53c in which the O-ring of the nozzle base part is engaged are both spherical surfaces having substantially the same curvature. However, as long as the operation of the present invention can be achieved, both have a curved surface in which the curvatures of the two change correspondingly (match) with each other instead of the spherical surface. May be.

  In addition, based on FIGS. 1 to 3, it has been described that the nozzle body 50 rotates about 90 ° around the nozzle shaft by rotating about 90 ° around the output shaft of the first and second motors 20. However, the angle range is not necessarily limited.

  The motor used in the present invention is not limited to the stepping motor as in the above-described embodiment, and various motors such as a (brush, brushless) DC motor can be used. Further, the arrangement of the motor is not limited to the arrangement as in the present embodiment, and any arrangement may be used as long as the operation range of the nozzle body 50 is not hindered.

  Further, the modules and the number of teeth of the first bevel gear 31 and the second bevel gear 32 and the third bevel gear 33 may be different from those of the above-described embodiment as long as the modules are the same.

  Specifically, if the gear modules are the same and “the number of teeth of the first and second bevel gears> the number of teeth of the third bevel gear”, the first and second motors are rotated at a constant rotational speed. However, “the rotational angular velocity of the coolant nozzle around the output axis of the first and second motors <the rotational angular velocity of the coolant nozzle around the nozzle shaft”.

  On the other hand, if the gear modules are the same and “the number of teeth of the first and second bevel gears <the number of teeth of the third bevel gear”, even if the first and second motors are rotated at a constant rotational speed, “Rotational angular velocity of the coolant nozzle around the output axis of the first and second motors> Rotational angular velocity of the coolant nozzle around the nozzle shaft”. Accordingly, by changing the number of teeth of the first and second bevel gears and the number of teeth of the third bevel gear, it is possible to cope with supply specifications of various grinding fluids and coolant fluids.

  Subsequently, a modification according to the above-described embodiment will be described. In addition, except the arrangement structure of the fixed shaft in the modification according to the present embodiment, it is the same as the above-described embodiment. Therefore, the arrangement structure of the fixed shaft, which is different from the above-described embodiment, will be described, and the same configuration as that of the above-described embodiment will be denoted by the corresponding reference numerals and detailed description thereof will be omitted. FIG. 4 is a front view showing a modification of the grinding fluid supply structure 2 to the two-way operation coolant nozzle according to the present embodiment.

  The fixed shaft 210 has a spherical fixed shaft protruding portion 211 at the distal end of the fixed shaft in the longitudinal direction. The fixed shaft 210 has a hose connecting portion 260 at one end (lower side in FIG. 4), and a hose (not shown here) for supplying a grinding fluid from a grinding fluid supply source (not shown) to the grinding fluid supply path 210a. Are connected to the hose connection 260. The fixed shaft 210 is supported so that the fixed shaft itself does not rotate and displace via fixing means (not shown) provided in the base 228 on which the motor 220 and the like are mounted.

  The grinding fluid supply path 210a is formed inside the fixed shaft and extends from one end (lower side in FIG. 4) of the fixed shaft 210 to the projecting portion side opening 211a for supplying the grinding fluid formed in the fixed shaft protruding portion 211. doing. That is, a grinding liquid supply path is formed from one end (lower side in FIG. 1) of the fixed shaft 210 through the grinding liquid supply path 210a to the protruding portion side opening 211a of the fixed shaft protruding portion 211, and the grinding liquid is supplied to the nozzle base 253. It is a communication hole to supply to.

  In this modification, a first bevel gear 231 and a second bevel gear 232 are pivotally supported at the tips of the output shafts 225 (226, 227) of the first motor 221 and the second motor 222, respectively. The first to third bevel gears 230 (231, 232, 233) are rotated by driving 220. In the present embodiment, stepping motors are used for the first motor 221 and the second motor 222. Note that the same stepping motor is used for the first motor 221 and the second motor 222.

  By having such a configuration, the present modification exhibits the same effect as the above-described embodiment. In addition, since an extra drive gear and solid shaft frame are not required as in the above embodiment, the number of components can be reduced, which contributes to cost reduction. Further, unlike the above-described embodiment, the grinding fluid supply path formed inside the fixed shaft is not bent, so that the grinding fluid is stably supplied to the nozzle tip 251 via the grinding fluid supply path 250a without causing pulsation or the like. it can.

  The shapes, dimensions, numerical values, and materials of the components introduced in the above-described embodiments are merely examples, and various shapes, dimensions, numerical values, and materials can be selected as appropriate without departing from the scope of the present invention. Needless to say.

  In the present embodiment, the grinding fluid is supplied from the nozzle tip of the coolant nozzle to the workpiece or tool of the machine tool. However, the present invention is not necessarily limited to such a grinding fluid. The polishing liquid, the cooling liquid (coolant liquid), and the cooling oil (coolant oil) may be supplied from the tip of the coolant nozzle to the workpiece or tool of the machine tool.

DESCRIPTION OF SYMBOLS 1 Grinding fluid supply structure to 2 direction operation | movement coolant nozzle 10 Fixed shaft 10a Grinding fluid supply path 11 Fixed shaft protrusion part 11a Projection part side opening part 21, 22 (20) Motor 31, 32, 33 (30) Bevel gear 40 Bracket 50 Nozzle body 50a Grinding fluid supply path 51 Nozzle tip 52 Nozzle shaft 53 Nozzle base 53a Nozzle side inflow hole 53b Flange 53c Engaging groove 80 O-ring (elastic seal member)

Claims (3)

In a two-way operation coolant nozzle that supplies grinding fluid or coolant fluid to workpieces and tools of machine tools,
A hemispherical or spherical fixed shaft protrusion is provided on a part of the fixed shaft in which the flow path for supplying the grinding liquid is formed,
The fixed shaft protrusion includes a communication hole for feeding the grinding liquid to the rotatable nozzle body,
The nozzle base formed in the funnel shape of the nozzle body is disposed to face the fixed shaft protruding portion, and the nozzle base can rotate around the nozzle axis while the fixed shaft protrusion is fixed. And is movable along the peripheral surface of the fixed shaft protrusion,
Between the fixed shaft protrusion and the nozzle base is sealed by an elastic seal member,
A two-way operation coolant characterized in that the grinding fluid is fed in a liquid-tight manner from the fixed shaft to the nozzle tip through the seal member regardless of the relative position of the fixed shaft protrusion and the nozzle base. Grinding fluid supply structure to the nozzle.   The structure for supplying a grinding fluid to the two-way operation coolant nozzle according to claim 1, wherein an engagement groove for holding the elastic seal member is formed in the nozzle base portion or the fixed shaft protruding portion. The virtual curved surface formed by the movement locus of the elastic seal member provided in the nozzle base is formed corresponding to the curved surface of the surface of the fixed shaft protruding portion along the elastic seal member of the fixed shaft protruding portion. The structure for supplying a grinding fluid to the two-way operation coolant nozzle according to claim 1,

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