JP2011169154A - Pump tappet - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lightweight and compact pump tappet having a locking pin structure which can prevent/suppress the abrasion of a recessed groove formed in a guide hole caused by reciprocating motion of the tappet even if the recessed groove formed in the guide hole and allowing the locking pin of the pump tappet to slide therewith is formed of soft material such as aluminum. <P>SOLUTION: The locking pin 24 of the tappet, sliding in the recessed groove 16b formed in the guide hole 16, is rotated with a segment in a direction perpendicular to a tappet sliding direction as a rotating shaft, and the locking pin 24 and the recessed groove 16b formed in the guide hole 16 are brought into not sliding contact but rolling contact with each other. Accordingly, the abrasion of the recessed groove 16b formed in the guide hole 16 is prevented or suppressed. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a pump tappet.

  In an automobile direct injection engine, a high pressure fuel pump is used to inject high pressure fuel into a cylinder. The high-pressure fuel pump converts the rotational motion of the camshaft provided with the cam to the reciprocating linear motion of the pump plunger, and feeds fuel by the reciprocating linear motion of the pump plunger to increase the pressure in the high-pressure chamber and into the combustion chamber. Fuel is supplied by injection. As a constituent member of the high-pressure fuel pump, there is a pump tappet that transmits the rotational motion of the camshaft to the pump plunger as a reciprocating linear motion.

  A technique related to a high-pressure pump including a tappet is disclosed in DE 10 2005 047 234 A1 (Patent Document 1). FIG. 18 is a cross-sectional view showing a part of the high-pressure pump of Patent Document 1 including a roller-filled tappet.

  The high-pressure pump shown in Patent Document 1 is in contact with a camshaft 1 that rotates in the direction of arrow A in FIG. 18, a cam 2 provided on the outer diameter side of the camshaft, and the cam 2. The rotary motion of the camshaft 1 is transmitted as a reciprocating linear motion to a pump plunger 3 (hereinafter simply referred to as “plunger”), and the tappet 4 that performs the reciprocating linear motion and the reciprocating linear motion in contact with the tappet 4 are performed. The plunger 3 as a rod-shaped member, a high-pressure chamber (not shown) for sending fuel according to the reciprocating linear motion of the plunger 3 and increasing pressure, and the tappet 4 are in contact with each other, and the plunger 3 is arranged on the inner side. A spring 5 provided in this way, and a housing 6 that accommodates the tappet 4, the plunger 3, and the spring 5 are provided.

  The tappet 4, the plunger 3 and the spring 5 are arranged so as to be accommodated in a guide hole 7 provided in the housing 6. The tappet 4 is guided on the inner diameter surface of the guide hole 7 in the vertical direction in FIG. 18, that is, in the direction of the arrow XVIII in FIG.

  The camshaft 1 and the tappet 4 are arranged so that the outer diameter surface of the cam 2 and the outer diameter surface of the outer ring 8 a of the roller bearing 8 accommodated in the tappet 4 are in contact with each other. One end portion 3 a of the plunger 3 is disposed so as to contact an intermediate bottom provided in the case 9 that is a constituent member of the tappet 4. The spring 5 is arranged so that one end thereof is in contact with a spring seat 10 provided on the lower side of the intermediate bottom.

A concave groove 7a extending in the direction of arrow XVIII in FIG. 18 is provided on the inner diameter surface of the guide hole 7 of the housing where the tappet 4 moves up and down so as to be recessed from the inner diameter surface. An anti-rotation pin 9 a is attached to the outer surface of the case 9 of the tappet 4 so as to protrude from the outer surface of the case 9 of the tappet 4, and the inner diameter of the guide hole 7 of the housing 7 is accommodated in the guide hole 7 of the tappet 4. The tappet 4 is prevented from rotating in the circumferential direction in the guide hole 7 by accommodating the rotation prevention pin 9a of the case 9 in the concave groove 7a provided on the surface.
The rotation prevention pin 9 a attached to the case 9 has a semi-cylindrical shape, and is press-fitted and fixed in an attachment hole 9 b formed in the peripheral wall of the case 9.

  A tappet 4 having such a detent pin 9a is also disclosed in Japanese Patent No. 3823819 (FIG. 4 of Patent Document 2), and has a structure as shown in FIG. Note that the tappet 4 of FIG. 19 has basically the same structure as the tappet 4 shown in FIG.

  These conventional locking pins 9a of the tappet 4 slide while sliding on the concave groove 7a of the guide hole 7 while receiving the force that the tappet 4 tries to rotate in the circumferential direction.

  However, the guide hole 7 is often provided in the cylinder head or cylinder head cover of the engine, and the material of the cylinder head or cylinder head cover of the engine is mainly aluminum. There is a risk of wearing the groove 7a.

  In order to solve such a problem of wear, as shown in FIG. 20, by attaching a roller 9c to the detent portion, the contact with the concave groove 7a of the guide hole 7 is a rolling contact, thereby suppressing the wear. Is disclosed in Japanese Utility Model Publication No. 62-16211 (Patent Document 3). The high-pressure pump shown in FIG. 20 has the same basic structure as that of the high-pressure pump shown in FIG.

DE 10 2005 047 234 A1 Japanese Patent No. 3823819 Japanese Utility Model Publication No. 62-162311

  However, as shown in FIGS. 20A and 20B, the tappet 4 disclosed in Patent Document 3 has a problem that the structure is complicated and the cost is increased. Further, a space for holding the roller 9c is required in the tappet 4, leading to an increase in size and weight of the tappet 4. When the weight of the tappet 4 increases, the inertial force when the tappet 4 reciprocates increases, and there is a possibility that the pump cannot be driven efficiently due to jumping.

  Therefore, the present invention prevents wear of the groove of the guide hole due to the reciprocating motion of the tappet, even if the groove of the guide hole in which the detent pin of the tappet slides is formed of a soft material such as aluminum. It is an object of the present invention to provide a lightweight and compact pump tappet having a detent pin structure that can be suppressed.

  In order to solve the above-mentioned problems, the present invention is provided with a detent pin accommodated in a concave groove formed in an inner diameter surface of a guide hole of a housing on the outer surface of a case accommodating a shaft and an outer ring. In the pump tappet provided with the mounting hole of the case on the peripheral wall of the case, the rotation prevention pin in the groove of the guide hole can be rotated about a line segment perpendicular to the sliding direction of the case as a rotation axis It is a thing.

  In this way, when the rotation prevention pin in the groove of the guide hole is made rotatable, the rotation prevention pin and the groove of the guide hole are not in sliding contact but in rolling contact, thereby preventing wear of the groove in the guide hole. -It can be suppressed.

And as means for enabling rotation of the detent pin in the concave groove of the guide hole, there are the following means.
The first is a fixed shaft portion for fixing the rotation prevention pin to the mounting hole of the case by press fitting, a bearing shaft portion projecting from the fixed shaft portion to the concave groove side of the guide hole, and an outer surface of the bearing shaft portion. The ring portion of the rotation prevention pin is made rotatable in the concave groove of the guide hole.

  The anti-rotation pin is formed by a mounting shaft portion that is inserted into the mounting hole of the case and a head portion that protrudes from the mounting shaft portion toward the concave groove side of the guide hole, and the mounting shaft portion is mounted on the case. It is also possible to employ a means for enabling rotation of the detent pin within the groove of the guide hole by being rotatably attached to the hole. And as a means for mounting the mounting shaft portion rotatably with respect to the mounting hole of the case, in addition to a method of projecting the end portion of the mounting shaft portion inside the case and caulking the protruding portion, A method of fitting a retaining ring or a method of inserting a knock pin can be employed.

  Further, a bearing member may be incorporated in the rotating portion of the rotation stopper pin.

  This bearing member can be configured by incorporating only a rolling bearing such as a roller bearing or a rolling element. In addition, a resin or metal sliding bearing may be employed as the bearing member.

  Moreover, you may make resin at least one component by the side of a shaft or a hole among the rotation parts of the said detent | locking pin.

  Furthermore, you may comprise at least one component by the side of a shaft or a hole among oil-impregnated sintered metals among the rotation parts of the said non-rotating pin.

  As described above, according to the present invention, the rotation prevention pin and the groove of the guide hole are not in sliding contact but in rolling contact by enabling rotation of the rotation prevention pin in the groove of the guide hole. It is possible to prevent / suppress wear of the concave grooves.

It is sectional drawing which shows a part of high-pressure pump containing the tappet which concerns on one Embodiment of this invention. It is a vertical front view of the tappet contained in the high pressure pump shown in FIG. It is a vertical side view of the tappet contained in the high pressure pump shown in FIG. FIG. 4 is a perspective view of the tappet shown in FIGS. 2 and 3. It is the figure which looked at the tappet shown in FIG. 4 from the direction of arrow V in FIG. It is the figure which looked at the tappet shown in FIG. 4 from the direction of arrow VI in FIG. It is the figure which looked at the tappet shown in FIG. 4 from the direction of arrow VII in FIG. It is the figure which looked at the tappet shown in FIG. 4 from the direction of arrow VIII in FIG. It is an enlarged vertical plan view showing an example of a detent pin. It is an enlarged vertical plan view showing another example of the rotation stopper pin. It is an enlarged vertical plan view showing another example of the rotation stopper pin. It is an enlarged vertical plan view showing another example of the rotation stopper pin. It is an enlarged vertical plan view showing another example of the rotation stopper pin. It is an enlarged vertical plan view showing another example of the rotation stopper pin. It is an enlarged view of the part shown by XV of the tappet shown in FIG. It is the figure which looked at a part of roller bearing contained in the tappet shown in FIG. 2 from the direction of arrow XVI in FIG. FIG. 16 is a partial cross-sectional view of a roller bearing included in the tappet illustrated in FIG. 2, which is a cross-sectional view taken along XVII-XVII in FIG. 15. It is sectional drawing which shows a part of high pressure pump containing the conventional tappet. It is a front view which shows the other example of the conventional tappet. (A) is sectional drawing which shows a part of other example of the conventional high pressure pump, (b) is a perspective view of the tappet of the example.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
A high pressure pump 11 including a tappet according to an embodiment of the present invention has a cam 12a provided on the outer diameter side thereof, a camshaft 12 that rotates in the direction of arrow A in FIG. The tappet 21 that abuts and transmits the rotary motion of the camshaft 12 as a reciprocating linear motion to the pump plunger 13 (hereinafter simply referred to as “plunger”) and performs the reciprocating linear motion, and the reciprocating linear motion abutting the tappet 21. Plunger 13 as a rod-shaped member that moves, a high-pressure chamber (not shown) that feeds fuel according to the reciprocating linear motion of plunger 13, abuts against tappet 21, and moves plunger 13 inward. A spring 14 provided so as to be disposed; and a housing 15 that accommodates the tappet 21, the plunger 13, and the spring 14. That.

  The tappet 21, the plunger 13 and the spring 14 are arranged so as to be accommodated in a guide hole 16 provided in the housing 15. The tappet 21 is guided by the inner diameter surface 16a of the guide hole 16 in the vertical direction in FIG. 1, that is, in the direction of the arrow I in FIG.

  The camshaft 12 and the tappet 21 are arranged so that the outer diameter surface 12b of the cam 12a and the outer diameter surface 32a of the outer ring 32 of the roller bearing 31 included in the tappet 21 abut. One end 13 a of the plunger 13 is disposed so as to abut on an intermediate bottom 23 c provided in a case 23 included in the tappet 21. The spring 14 is arranged so that one end thereof is in contact with a spring seat 17 provided on the lower side of the intermediate bottom 23c.

  The spring 14 has an elastic force in the downward direction, that is, in the direction opposite to the direction indicated by the arrow I in FIG. The tappet 21 is urged upward by the elastic force of the spring 14 in the upward direction, that is, in the direction indicated by the arrow I in FIG.

  The tappet 21 and the plunger 13 are moved in the vertical direction, that is, in the direction of the arrow I in FIG. 1 or vice versa by the rotational movement of the camshaft 12, the urging of the spring 14, and the guide of the inner diameter surface 16a of the guide hole 16. Reciprocating linear motion in the direction of. The reciprocating linear motion here is a motion in the direction of arrow I in FIG. 1 or in the opposite direction. When the camshaft 12 rotates at a high speed, the speed of the reciprocating linear motion of the tappet 21 and the plunger 13 also increases.

  The high pressure chamber is disposed on the other end side (not shown) of the plunger 13. The reciprocating linear motion of the plunger 13 can increase the pressure of the fuel supplied to the high pressure chamber.

  Next, the configuration of the tappet 21 according to an embodiment of the present invention will be described. The tappet 21 includes a shaft 22, a roller bearing 31 that is disposed on the outer diameter side of the shaft 22 and is rotatably supported on the shaft 22, and a case 23 that houses the shaft 22 and the roller bearing 31.

  The case 23 includes a cylindrical peripheral wall 23a and an intermediate bottom 23c provided at an intermediate position on the inner diameter surface 23b of the peripheral wall 23a so as to partition the space in the vertical direction. Of the case 23, the intermediate bottom 23 c is in contact with the plunger 13. The peripheral wall 23a and the intermediate bottom 23c have a predetermined thickness.

  As shown in FIG. 3, a pair of support holes 23d and 23e that support both ends of the shaft 22 are provided on one end side of the peripheral wall 23a. The shaft 22 is arranged so that the shaft 22 is inserted into the pair of support holes 23d and 23e. A roller bearing 31 is disposed on the outer diameter side of the shaft 22. Thus, the case 23 accommodates the shaft 22 and the roller bearing 31 in the space 23f from the intermediate bottom 23c toward the one end side of the peripheral wall 23a.

  The shaft 22 is formed in a hollow shape, and is fixed to the support holes 23d and 23e by caulking and fixing the outer peripheral edge portion of the end surface of the shaft 22. Reference numeral 22a indicates a caulking portion. By making the shaft 22 hollow, the weight can be reduced as compared with the case of using a solid shaft.

  A part of the plunger 13 is accommodated in the space 23g from the intermediate bottom 23c toward the other end side of the peripheral wall 23a. Specifically, the one end portion 13a of the plunger 13 is disposed so as to contact the central portion in the radial direction of the intermediate bottom 23c, and the one end portion 13a of the plunger 13 is accommodated. Note that one end of the spring 14 is also accommodated in the space 23g.

  The middle bottom 23c is provided with four oil holes 25 penetrating in the thickness direction (see FIGS. 7 and 8). The four oil holes 25 are provided so as to avoid a contact portion between the one end portion 13a of the plunger 13 and the intermediate bottom 23c. By using this oil hole 25, the lubricating oil supplied to the tappet 21 can be passed between the space 23f and the space 23g.

  As shown in FIG. 2, the case 23 is provided with a mounting hole 23i as a recess penetrating from the outer diameter surface 23h to the inner diameter surface 23b of the peripheral wall 23a. An anti-rotation pin 24 is attached to the attachment hole 23i so that a part of the attachment hole 23i protrudes from the outer diameter surface 23h.

  As shown in FIG. 5, the rotation prevention pin 24 is attached to the case 23 so as to be rotatable about a line segment perpendicular to the sliding direction of the case 23 as a rotation axis.

  As described above, when the rotation prevention pin 24 accommodated in the groove 16b of the guide hole 16 is rotatable, the rotation prevention pin 24 and the groove 16b of the guide hole 16 are not in sliding contact but in rolling contact. The wear of the concave groove 16b of the guide hole 16 can be prevented / suppressed.

  As means for enabling rotation of the rotation prevention pin 24 in the concave groove 16 of the guide hole 16, the following means can be employed.

  As shown in FIG. 9, the first means is that the rotation prevention pin 24 is fixed to the mounting hole 23i of the case 23 by press-fitting, and the guide shaft 16 is recessed from the fixed shaft 24a. By configuring the bearing shaft portion 24b protruding to the groove 16b side and the ring portion 24c rotatably attached to the outer surface of the bearing shaft portion 24b, the rotation prevention pin 24 is configured in the recessed groove 16 of the guide hole 16. The ring portion 24c, which is a member, is made rotatable. At the tip of the bearing shaft portion 24b, a flange portion 24d for preventing the ring portion 24 from coming off is provided.

  As shown in FIG. 10, a bearing member 24e may be inserted into the rotating portion of the bearing shaft portion 24b and the ring portion 24c. As the bearing member 24e, in addition to a rolling bearing such as a roller bearing, a sliding bearing made of resin or metal may be used, or only a rolling element is incorporated between the bearing shaft portion 24b and the ring portion 24c. Also good.

  FIG. 11 is a modification of the example of FIG. In the embodiment of FIG. 9, the cross-sectional shape of the groove 16b of the guide hole 16 is semicircular, and the outer surface shape of the ring portion 24c of the detent pin 24 accommodated in the groove 16b is correspondingly formed. In contrast to the hemispherical shape, in the embodiment of FIG. 11, the shape of the cross section of the concave groove 16b of the guide hole 16 and the shape of the outer surface of the ring portion 24 are each formed in a square shape.

  Next, as shown in FIG. 12, the second means for enabling rotation of the rotation prevention pin 24 in the concave groove 16 of the guide hole 16 is to insert the rotation prevention pin 24 into the mounting hole 23i of the case 23. The mounting shaft portion 24f and the head portion 24g projecting from the mounting shaft portion 24 toward the concave groove 16b of the guide hole 16 can be rotated with respect to the mounting hole 23i of the case 23. It is means to attach to. Thus, if the attachment shaft portion 24f is rotatably attached to the attachment hole 23i of the case 23, the number of parts can be reduced as compared with the embodiment using the ring portion 24c of FIG. Can be planned.

  Then, as means for attaching the mounting shaft portion 24f to the mounting hole 23i of the case 23 so as to prevent it from coming off, the end portion of the mounting shaft portion 24f protrudes to the inside of the case 23, and FIG. As shown in FIG. 4, a method of caulking the protruding portion can be employed. Reference numeral 24h in FIG. 12 indicates the caulking portion. In addition to this caulking method, as shown in FIG. 13, in addition to the method of fitting a retaining ring 24i to the protruding portion of the mounting shaft portion 24f, a knock pin is inserted into the protruding portion of the mounting shaft portion 24f, so that the mounting shaft portion 24 is You may attach so that it may not come out in the state which can be rotated with respect to the attachment hole 23i.

  Further, as shown in FIG. 14, a bearing member 24j may be incorporated between the mounting shaft portion 24f and the mounting hole 23i of the case 23. As the bearing member 24j, in addition to a rolling bearing such as a roller bearing, a sliding bearing made of resin or metal may be used, or only a rolling element is provided between the mounting shaft portion 24f and the mounting hole 23i of the case 23. You may make it the structure to incorporate.

  Of the rotating portion of the locking pin 24, for example, in the embodiment of FIGS. 9 and 11, one of the bearing shaft portion 24b and the ring portion 24c may be made of resin or oil-impregnated sintered metal. When the mounting shaft portion 24f rotates inside the mounting hole 23i as in the embodiment of FIGS. 12 and 13, the inside of the mounting shaft portion 24f or the mounting hole 23i is made of resin or oil-impregnated sintered metal. May be.

  Next, the configuration of the roller bearing 31 included in the tappet 21 will be described. FIG. 15 is an enlarged view of a portion indicated by XV of a two-dot chain line in FIG. A roller pitch circle 31a is shown by a one-dot chain line in FIG. FIG. 16 is a view of a part of the roller bearing 31 as seen from the direction of the arrow XVI shown in FIG. FIG. 17 is a cross-sectional view showing a part of the roller bearing 31, which is a cross-section XVII-XVII in FIG. 15. The roller bearing 31 includes an outer ring 32, a plurality of rollers 33 disposed between the outer ring 32 and the shaft 22, and a cage 34 that holds the plurality of rollers 33.

  The retainer 34 includes a pair of annular portions 34 a and 34 b and a plurality of column portions 34 d that connect the pair of annular portions 34 a and 34 b so as to form a pocket 34 c that accommodates the rollers 33. The column portion 34d has a shape extending straight in the axial direction, that is, in the cross section shown in FIG.

  Similar to the rollers 33, the retainer 34 is disposed between the outer ring 32 and the shaft 22. The plurality of rollers 33 and the respective cages 34c provided in the cage 34 are respectively accommodated and held. The retainer 34 is configured such that the outer diameter guide, that is, the inner diameter surface 32 b of the outer ring 32 disposed on the outer diameter side of the retainer 34 and the outer diameter surface 34 e of the retainer 34 are in radial contact. Further, the retainer 34 is provided with an oil groove 34f so as to be recessed inward from the outer diameter surface 34e. The oil groove 34f is provided at the center of the column portion 34d and has a shape extending in the circumferential direction.

  Due to the rotational movement of the camshaft 12, the outer ring 32 and the rollers 33, which are constituent members of the roller bearing 31, are also rotated. When the camshaft 12 rotates at a high speed, the rotation of the rollers 33 also increases. Here, in the roller bearing 31 which is a constituent member of the tappet 21, the position of the roller 33 in the roller bearing 31 at the time of high speed rotation can be stabilized by the cage 34. Then, the skew of the roller 33 can be suppressed and the lateral running of the roller bearing 31 can be prevented. Accordingly, it is possible to reduce the risk of poor lubrication of the roller bearing 31 and wear of the roller bearing 31 during high-speed rotation. That is, such a pump tappet can be manufactured at a low cost, and can be increased in speed and life.

  Further, such a high-pressure pump 11 includes a tappet 21 that can be manufactured at a low cost and can reduce the risk of poor lubrication of the roller bearing 31 and wear of the roller bearing 31 during high-speed rotation. The fuel can be manufactured at a low cost, and the pressure of the fuel can be increased more stably in a short time.

  Here, the retainer 34 is an outer diameter guide, and the retainer 34 and the outer ring 32 are provided on the outer diameter surface 34e of the retainer 34 because an oil groove 34f that is recessed inward from the surface is provided. And the radial position of the cage 34 can be stabilized. Further, the oil permeability of the inner diameter surface 34g of the cage 34 and the outer diameter surface 22a of the shaft 22 is improved, and the lubricity between the outer diameter surface 34e of the cage 34 and the inner diameter surface 32b of the outer ring 32 is improved and retained. Wear of the vessel 34 and the outer ring 32 can be suppressed. Therefore, the life of the cage 34, the rollers 33, the outer ring 32, and the shaft 22 can be extended. The oil groove may be provided so as to extend with an inclination in the axial direction, or may be provided so as to extend in a curved manner. A plurality of oil grooves may be provided.

  The cage 34 is an inner diameter guide, and an oil groove may be provided on the inner diameter surface 34 g of the cage 34. By carrying out like this, the holder | retainer 34 and the shaft 22 can be made to contact and the radial position of the holder | retainer 34 can be stabilized. Further, the oil permeability of the outer diameter surface 34e of the cage 34 and the inner diameter surface 32b of the outer ring 32 is improved, and the lubricity between the inner diameter surface 34g of the cage 34 and the outer diameter surface 22a of the shaft 22 is improved and retained. Wear of the vessel 34 and the shaft 22 can be suppressed. Therefore, the life of the cage 34, the rollers 33, the outer ring 32, and the shaft 22 can be extended.

  The cage 34 provided in the roller bearing 31 may be made of resin. By carrying out like this, the holder | retainer 34 itself can be made lightweight and the weight of the tappet 21 can be lightened generally. Therefore, the force required for the reciprocating linear motion, here, the force required for the vertical movement of the tappet 21 can be reduced. Further, when the cage 34 is made of resin, it can be manufactured by injection molding or the like, so that mass production is facilitated and it can be manufactured at low cost. Examples of the material of the cage 34 include nylon 66, nylon 46, polyphenylene sulfide (PPS), polyether ether ketone (PEEK), and the like. If necessary, the resin may be filled with carbon fiber, glass fiber, carbon black, or the like.

  In FIG. 16, the dimension of the clearance between the rolling surface 33a of the roller 33 accommodated in the pocket 34c and the side wall surface 34h of the column portion 34d is exaggerated and enlarged for easy understanding. Yes.

  In addition, the roller and shaft which comprise the above-mentioned tappet are manufactured by forging, cutting, etc. of steel members, for example, SUJ2 and SCM420 (all are JIS standards).

  In the above-described embodiment, the cage includes a pair of annular portions and a plurality of pillar portions, but is not limited thereto, and is divided into a plurality of members instead of an integrated type, A spacer-type cage disposed between the rollers may be used.

  Moreover, in the said embodiment, although the pillar part was made into the shape extended straightly to an axial direction, it is not restricted to this, For example, the pillar part may be bent by radial direction, for example, a V-type holder, It may be shaped like an M-type cage. Furthermore, it is good also as providing the roller stop part which prevents the fall-off | omission of the roller of the radial direction on the side wall surface of a pillar part.

  In the above-described embodiment, the roller bearing is configured to include a cage that holds a plurality of rollers. However, the configuration is not limited thereto, that is, a configuration in which the roller bearing does not include a cage, that is, a full-roller type. The same applies to roller bearings.

  The above embodiment is the tappet 21 in which the roller bearing 31 is provided on the outer diameter side of the shaft 22, but the rolling element is omitted, and the outer ring 32 a is directly provided rotatably on the outer diameter side of the shaft 22. Good.

  As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

  The tappet according to the present invention is included in a high-pressure pump that supplies fuel to an engine such as an automobile, and is effectively used as a part for an automobile.

11 High-pressure pump 12 Cam shaft 12a Cam 13 Plunger 13a One end 15 Housing 16 Guide hole 16a Inner diameter surface 16b Groove 21 Tappet 22 Shaft 23 Case 23a Peripheral wall 23c Intermediate bottom 23i Mounting hole 24 Non-rotating pin 24a Fixed shaft portion 24b Bearing Shaft portion 24c Ring portion 24d Fence portion 24e Bearing member 24f Mounting shaft portion 24g Head portion 24h Caulking portion 24i Retaining ring 24j Bearing member 31 Roller bearing 32 Outer ring 33 Roller

Claims (14)

  The pump has a non-rotating pin accommodated in a concave groove formed in the inner diameter surface of the guide hole of the housing on the outer surface of the case accommodating the shaft and the outer ring, and the mounting hole for the detent pin is provided in the peripheral wall of the case A tappet for a pump, wherein the rotation preventing pin in the concave groove of the guide hole is rotatable about a line segment perpendicular to the sliding direction of the case as a rotation axis.   The pump tappet according to claim 1, wherein the rotation prevention pin and the concave groove of the guide hole are in rolling contact.   A fixed shaft portion for fixing the above-mentioned detent pin into the mounting hole of the case by press fitting, a bearing shaft portion protruding from the fixed shaft portion toward the concave groove side of the guide hole, and rotatably mounted on the outer surface of the bearing shaft portion The pump tappet according to claim 1, wherein the rotation stopper pin is rotatable in the concave groove of the guide hole.   The detent pin is formed by a mounting shaft portion that is inserted into the mounting hole of the case and a head portion that protrudes from the mounting shaft portion toward the concave groove side of the guide hole, and the mounting shaft portion is formed in the mounting hole of the case. The pump tappet according to claim 1, wherein the rotation prevention pin is rotatable in the concave groove of the guide hole by being rotatably attached to the guide.   5. The pump according to claim 4, wherein the mounting shaft portion protrudes inward of the case, and the protruding portion is caulked so that the mounting shaft portion is mounted so as not to come out in a rotatable state with respect to the mounting hole. Tappet.   The mounting shaft portion is protruded inward of the case, and a retaining ring is fitted to the protruding portion, so that the mounting shaft portion can be attached to the mounting hole so as not to come off in a rotatable state. 4. The tappet for pumps according to 4.   5. The mounting shaft portion is protruded inward of the case, and a knock pin is inserted into the protruding portion so that the mounting shaft portion is mounted so as not to come off in a rotatable state with respect to the mounting hole. Tappet for pump as described in 1.   The tappet for a pump according to any one of claims 1 to 7, wherein a bearing member is attached to a rotating portion of the detent pin.   The pump tappet according to claim 8, wherein the bearing member is a rolling bearing.   The pump tappet according to claim 8, wherein the bearing member is a sliding bearing.   The pump tappet according to any one of claims 1 to 7, wherein at least one member on a rotation stopper pin side or an attachment hole side constituting a rotation part of the rotation prevention pin is made of resin.   The tappet for a pump according to any one of claims 1 to 7, wherein at least one member on the side of the locking pin or the mounting hole constituting the rotating part of the locking pin is made of oil-impregnated sintered metal. .   A high-pressure fuel pump using the pump tappet according to any one of claims 1 to 12. An automobile or a motorcycle using the high-pressure fuel pump according to claim 13.

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