JP5460906B2 - High pressure pump - Google Patents

Description

  The present invention relates to a high-pressure pump used for an internal combustion engine.

Conventionally, a high-pressure pump that supplies fuel to a fuel supply system of an internal combustion engine is known. The fuel pumped up from the fuel tank is sucked into the pressurizing chamber by the lowering of the plunger in the cylinder hole of the high pressure pump, and is metered and pressurized by the raising of the plunger.
By the way, in the process of assembling such a high-pressure pump and the process of mounting the assembled high-pressure pump on the engine, it is necessary to prevent the plunger inserted into the cylinder hole from dropping from the cylinder hole.

Also in the fuel high-pressure pump described in Patent Document 1 and the fuel pump device described in Patent Document 2, measures are taken to prevent the plunger from dropping from the cylinder hole. For example, Patent Document 1 describes that the stepped portion 48 of the piston 36 previously inserted into the casing 28 cooperates with the stopper 78 of the stopper element 60 fixed to the casing 28 (patent). (See claim 1 of FIG. 1 and FIG. 2).
Also, US Pat. No. 6,057,836 limits the range of outward movement of the plunger 12 by a cradle in the form of an annulus 23 that engages the tongue 17 so that during transport and assembly of the device to the associated engine. Among them, it is described that the plunger 12 is prevented from falling from the hole 11 (see paragraph [0010] of Patent Document 2 and FIGS. 1 and 2).

Special table 2008-525713 JP-A-4-231673

Incidentally, in the fuel high-pressure pump described in Patent Document 1, as is apparent from FIG. 2, the annular step 48 at the boundary between the large-diameter region 44 and the small-diameter region 46 of the piston 36 has a stopper element 60. When contacting the stopper 78, the outer peripheral wall surface of the region 44 having a large diameter of the piston 36 that slides with the inner wall surface of the piston bush 34, that is, a part of the sliding surface is exposed from the piston bush 34. .
For this reason, when the step 48 of the piston 36 contacts the stopper 78, a dent is formed on the exposed sliding surface of the piston 36, and the sliding surface of the piston 36 may be deformed by the dent. Further, there is a possibility that foreign matter or the like may adhere to the exposed sliding surface of the piston 36. In either case, the problem of poor sliding of the piston 36 occurs.

Further, in the fuel pump device described in Patent Document 2, as is apparent from FIGS. 1 and 2, the pedestal in the shape of the annular ring 23 that limits the range of the outward movement of the plunger 12 forms the hole 11. A portion of the outer peripheral wall surface of the plunger 12 that slides with the inner wall surface of the hole 11 when the plunger 12 abuts against the receiving base of the ring 23. However, it will be in the state exposed from the hole 11.
For this reason, also in the fuel pump device described in Patent Document 2, as in the case of the fuel high-pressure pump described in Patent Document 1, due to dents or foreign matter adhesion on the exposed sliding surface of the plunger 12, etc. The problem of poor sliding of the plunger 12 occurs.
Furthermore, in the fuel pump device described in Patent Document 2, the physique of the stopper structure that prevents the plunger 12 from falling from the hole 11 is very large, and is defined in the use of the fuel pump device. However, there is a problem that the stopper structure is not considered to be separated from the engine oil region when the fuel region is provided on the lower end side of the plunger 12.

  The present invention has been made in view of the above problems, and in the process of assembling the high-pressure pump, the process of mounting the assembled high-pressure pump on the engine, and the operation of the assembled high-pressure pump, An object of the present invention is to provide a high-pressure pump that prevents a plunger from dropping from a cylinder hole and sliding failure in a state where it is protected from foreign matter adhesion.

According to the first aspect of the present invention, the cylinder forming member is formed with the cylinder hole and the pressurizing chamber communicating with the cylinder hole. The plunger that reciprocates in the cylinder hole in the axial direction has a sliding surface that slides along the inner wall surface of the cylinder hole, and sucks and pressurizes fuel into the pressurizing chamber by reciprocating movement in the cylinder hole.
A plunger stopper is detachably attached to a cylinder hole forming portion that includes a cylinder end portion on the opposite side of the pressurizing chamber of the cylinder forming member and protrudes to the opposite side of the pressurizing chamber. The plunger stopper cooperates with a stepped portion formed at a predetermined position of the plunger, and regulates the movement of the plunger in a state where the sliding surface of the plunger is in contact with the inner wall surface of the cylinder hole.

  Thus, in the high pressure pump according to the first aspect, the plunger stopper attached to the cylinder hole forming portion (specifically, near the cylinder end portion) cooperates with the stepped portion formed at a predetermined position of the plunger. Then, the movement of the plunger in the cylinder hole is restricted. As a result, the plunger stopper functions as a stopper when the plunger reciprocates in the cylinder hole during operation after assembling the high-pressure pump, particularly when it descends from the top dead center to the bottom dead center. Fulfill. In addition, the stopper functions to prevent the plunger from dropping from the cylinder hole in the process of assembling the high-pressure pump and in the process of mounting the assembled high-pressure pump on the engine.

  Further, since the plunger stopper is detachably attached to the cylinder hole forming portion of the cylinder forming member, the convenience in handling particularly in the assembly process of the high-pressure pump and the engine mounting process is enhanced.

  In addition, this plunger stopper restricts the movement of the plunger with the sliding surface of the plunger in contact with the inner wall surface of the cylinder hole, thereby reciprocating the plunger in the cylinder hole during operation after the high pressure pump is assembled. When sliding or preventing the plunger from dropping from the cylinder hole during the assembly process of the high-pressure pump or the engine mounting process, the sliding surface of the plunger should be protected to prevent dents and foreign matter from adhering to it. Retained.

The plunger has a large-diameter portion having an end facing the pressurizing chamber and a sliding surface, a small-diameter portion extending from the large-diameter portion to the opposite side of the pressurizing chamber and having a smaller outer diameter than the large-diameter portion, and a large-diameter portion. A first stepped portion that forms a boundary between the diameter portion and the small diameter portion. And this 1st step part becomes a step part which cooperates with a plunger stopper. The plunger stopper has a stopper portion with which the stepped portion comes into contact with the movement of the plunger in the cylinder hole.
Thus, the 1st step part which makes the boundary of the large diameter part and small diameter part of a plunger cooperated with the plunger stopper as a step part, and made the sliding surface of a plunger contact the inner wall surface of a cylinder hole. In the state, the movement of the plunger can be restricted.

Furthermore, the plunger stopper has a plurality of engaging portions that engage with the outer wall surface of the cylinder hole forming portion of the cylinder forming member.
Thus, the plunger stopper is detachably attached to the cylinder hole forming portion of the cylinder forming member by the plurality of engaging portions. Here, as a configuration of the plurality of engaging portions, for example, if three engaging portions are evenly arranged in the circumferential direction, the minimum number can be engaged with a good balance.

Furthermore, according to the invention which concerns on Claim 2, an engaging part is pressed by the outer wall surface of the cylinder hole formation part of a cylinder formation member with the elastic force to radial direction.
Thus, in the high pressure pump according to the second aspect, the plunger stopper is pressed against the outer wall surface of the cylinder forming member by the elastic force of the engaging portion, and is fixed so as to hold the outer wall surface. Accordingly, the plunger stopper can be detachably attached to the cylinder forming member without forming an outer recess on the outer wall surface of the cylinder forming member. Therefore, the manufacturing cost for forming the recess can be reduced.

According to the invention which concerns on Claim 3, it has a convex part contact | abutted to the cylinder edge part of a cylinder formation member between the circumferential directions of a some engaging part.
Thus, in the high pressure pump according to the third aspect, the upper surface of the convex portion of the plunger stopper is abutted against the cylinder end, whereby the plunger stopper is positioned in the axial direction with respect to the cylinder forming member.

According to the invention which concerns on Claim 4, the communicating path which connects the radial direction and the radial direction of a plunger stopper is formed between the circumferential directions of a some convex part.
Since the plunger of the invention according to claim 1 or less has the large diameter portion and the small diameter portion as described above, the plunger reciprocates between the inner wall surface of the cylinder hole and the outer wall surface of the small diameter portion. A variable volume chamber having a variable volume is formed. Specifically, the variable volume chamber is formed in the radially inward direction of the plunger stopper, and the volume obtained by multiplying the cross-sectional area difference between the large diameter portion and the small diameter portion of the plunger by the movement distance of the plunger changes. At this time, in the high-pressure pump according to the fourth aspect, since the communication path that connects the inner diameter direction and the outer diameter direction of the plunger stopper is formed, the fuel passes through the communication path according to the volume change of the variable volume chamber. Thus, it becomes easy to flow into and out of the variable volume chamber.

According to the invention which concerns on Claim 5, a stopper part is formed in the diameter inner side of the inner wall of a some convex part.
Thus, in the high pressure pump according to the fifth aspect, the “stopper portion with which the stepped portion comes into contact with the movement of the plunger in the cylinder hole” is formed on the inner diameter side of the inner wall of the convex portion. By forming the inner diameter of the virtual circle connecting the inner walls of the convex portions slightly larger than the diameter of the large diameter portion of the plunger, the large diameter portion of the plunger can be guided.

According to the invention which concerns on Claim 6, a plunger stopper is comprised from the 1st ring which has an engaging part, and the 2nd ring which has a convex part and is provided separately from a 1st ring.
In this way, the high pressure pump according to the sixth aspect includes, for example, a first ring formed by pressing or the like with a relatively thin plate material and a second ring formed by pressing or the like with a relatively thick plate material. Can be combined to form a plunger stopper. As a result, for example, a first ring that requires elasticity and a second ring that requires rigidity, for example, can be formed of a material having a thickness suitable for pressing. Therefore, the manufacturing efficiency of the plunger stopper can be improved and the total manufacturing cost can be reduced.

Furthermore, according to the invention which concerns on Claim 7, the engaging part of a 1st ring is formed so that it may extend from the outer edge part of a cyclic | annular main body to the pressurization chamber side of an axial direction. In addition, the second ring has a notch that can be engaged with at least a part of the engaging part at a position corresponding to the engaging part in the circumferential direction, and the engaging part is engaged with the notch. , Combined with the first ring.
Thus, in the high pressure pump according to the seventh aspect, at least a part of the engaging portion of the first ring of the plunger stopper is engaged with the notch portion of the second ring, so that the engaging portion is the second ring. Arranged inside the outer diameter. For this reason, a space can be used effectively. Further, the first ring and the second ring can be prevented from rotating. The engaging portion may further have a protrusion, an auxiliary claw, or the like for preventing the first ring and the second ring from being detached.

According to the invention which concerns on Claim 8, an outer recess is formed in the outer wall surface of the cylinder hole formation part of a cylinder formation member, and the plunger stopper is latched and attached to this outer recess.
Thus, the high pressure pump according to the eighth aspect of the present invention has the plunger stopper engaged with and attached to the outer recess formed on the outer wall surface of the cylinder hole forming portion of the cylinder forming member. Can be removed and removed by releasing the lock. That is, the plunger stopper can be attached to and detached from the cylinder forming member.

According to the ninth aspect of the present invention, the cylinder forming member is continuously integrated with the pump body that forms the outline of the high-pressure pump.
That is, even when a so-called cylinder-integrated pump body in which the cylinder forming member and the pump body are continuously integrated is used, the cylinder forming member is different from the pump body in the case of a so-called separate cylinder. However, the invention of the high-pressure pump according to claims 1 to 8 is applied.

  According to the invention of claim 10, the plunger has a large-diameter portion whose end portion faces the pressurizing chamber and has a sliding surface, and extends from the large-diameter portion to the opposite side of the pressurizing chamber and has an outer diameter larger than that of the large-diameter portion. A small-diameter medium diameter portion, a small-diameter portion extending from the medium-diameter portion to the opposite side of the pressurizing chamber and having a smaller outer diameter than the medium-diameter portion, and a second stepped portion that forms a boundary between the medium-diameter portion and the small-diameter portion ,have. And this 2nd stepped part turns into a stepped part which cooperates with a plunger stopper. The plunger stopper has a stopper portion with which the stepped portion comes into contact with the movement of the plunger in the cylinder hole. The distance between the stopper portion and the cylinder end of the cylinder forming member is the same as the axial length of the cylinder hole in the medium diameter portion, or alternatively, the distance in the axial direction of the cylinder hole in the medium diameter portion. short.

  Thus, in the high pressure pump according to the tenth aspect, the second stepped portion that forms the boundary between the middle diameter portion and the small diameter portion of the plunger becomes a stepped portion that cooperates with the plunger stopper, and the second stepped portion is The distance between the stopper portion of the abutting plunger and the cylinder end portion of the cylinder forming member is the same as the axial length of the cylinder hole in the medium diameter portion, or the axial length of the cylinder hole in the medium diameter portion When the second stepped portion of the plunger is in contact with the stopper portion of the plunger stopper, the sliding surface of the large diameter portion of the plunger is in contact with the inner wall surface of the cylinder hole. Become. Therefore, the sliding surface of the plunger can be protected more reliably.

  According to the eleventh aspect of the present invention, the fuel seal member that slidably contacts the outer wall surface of the middle diameter portion and suppresses fuel leakage accompanying the reciprocating movement of the plunger is provided near the cylinder end portion of the cylinder forming member and the plunger. It is arrange | positioned between the stopper parts of a stopper.

  Thus, in the high pressure pump according to the eleventh aspect, the fuel seal member is interposed between the boundary between the large diameter portion and the middle diameter portion and the stopper portion of the plunger stopper, so that the stopper portion of the plunger stopper is separated from the fuel region. Even if a small amount of foreign matter is generated when the second stepped portion of the plunger comes into contact with the stopper portion of the plunger stopper, the foreign matter is separated from the sliding surface of the large diameter portion and the cylinder hole. Intrusion between the inner wall surface and the inner wall surface is eliminated.

It is a schematic sectional drawing which shows the high pressure pump by 1st Embodiment of this invention. (A) is sectional drawing which shows the state by which the plunger stopper is attached to the plunger part of the high pressure pump of FIG. 1, (b) is a perspective view which shows the plunger stopper. It is sectional drawing which shows the state by which the plunger stopper is attached to the plunger part of the high pressure pump by the modification of 1st Embodiment of this invention. (A) is sectional drawing which shows the state by which the plunger stopper is attached to the plunger part of the high pressure pump by the reference form of this invention, (b) is a perspective view which shows the plunger stopper. It is a plunger part enlarged view of the high-pressure pump by a 3rd embodiment of the present invention. It is the perspective view of (a) 2nd ring and (b) 1st ring which comprise the plunger stopper by the basic example of 3rd Embodiment of this invention. It is the (a) perspective view which shows the plunger stopper by the basic example of 3rd Embodiment of this invention, (b) It is bb sectional drawing of (a). It is the (a) perspective view which shows the plunger stopper by the 1st modification of 3rd Embodiment of this invention, (b) It is bb sectional drawing of (a). It is (a) perspective view which shows the plunger stopper by the 2nd modification of 3rd Embodiment of this invention, (b) It is bb sectional drawing of (a). It is (a) perspective view which shows the plunger stopper by the 3rd modification of 3rd Embodiment of this invention, (b) It is bb sectional drawing of (a). It is (a) perspective view which shows the plunger stopper by the 4th modification of 3rd Embodiment of this invention, (b) It is bb sectional drawing of (a). It is (a) perspective view which shows the plunger stopper by the 5th modification of 3rd Embodiment of this invention, (b) It is bb sectional drawing of (a). It is (a) perspective view which shows the plunger stopper by the basic example of 4th Embodiment of this invention, (b) It is bb sectional drawing of (a). It is the (a) perspective view which shows the plunger stopper by the modification of 4th Embodiment of this invention, (b) It is bb sectional drawing of (a). It is sectional drawing which shows the state by which the plunger stopper is attached to the plunger part of the high pressure pump by 5th Embodiment of this invention. It is a schematic sectional drawing which shows the high pressure pump by 6th Embodiment of this invention.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
The high-pressure pump according to the first embodiment of the present invention is shown in FIG. 1, the state where the plunger stopper is attached to the plunger portion is shown in FIG. 2 (a), and the plunger stopper is shown in FIG. 2 (b).

First, the high-pressure pump 1 according to the present embodiment will be described with reference to FIG.
The high-pressure pump 1 is provided in a fuel supply system that supplies fuel to the internal combustion engine. The fuel pumped up from the fuel tank is pressurized by the high-pressure pump 1 and accumulated in the delivery pipe. The fuel is injected and supplied to each cylinder of the internal combustion engine from an injector connected to the delivery pipe.
The high-pressure pump 1 includes a pump body 10, a plunger unit 20, a damper chamber 40, a suction valve unit 50, an electromagnetic drive unit 60, a discharge valve unit 70, and the like. In this embodiment, the pump body 10 corresponds to a “cylinder forming member” recited in the claims.

(A) The pump body 10 and the plunger part 20 are demonstrated.
The pump body 10 is integrally formed with a cylindrical cylinder hole 11 and a pressurizing chamber 12 communicating with the cylinder hole 11. The cylinder hole forming portion 14 is a cylindrical portion that protrudes on the opposite side to the damper chamber 40 of the pump body 10, and includes a cylinder end portion 141 on the opposite side to the pressurizing chamber 12. Around the cylinder hole forming portion 14, a recess 13 is formed in a substantially annular shape in which a portion for locking the plunger spring 28 of the seal element 25 is accommodated.
An outer recess 15 is formed in a circumferential shape on the outer wall surface 142 which is the wall surface on the concave portion 13 side of the cylinder hole forming portion 14.

The plunger portion 20 includes a plunger 21, a plunger stopper 23, a fuel seal member 24, a seal element 25, a plunger spring 28, and the like.
The plunger 21 is accommodated in the cylinder hole 11 and is held so as to be capable of reciprocating in the central axis direction. The plunger 21 has one end facing the pressurizing chamber 12, a large-diameter portion 211 that slides along the inner wall constituting the cylinder hole 11, and an outer diameter smaller than the large-diameter portion 211. It has a small diameter part 213 extending from the diameter part 211 to the opposite side of the pressurizing chamber 12 side. The large diameter portion 211 and the small diameter portion 213 have a coaxial shape, and a stepped portion 214 is formed at the boundary. A spring seat 27 is provided at the end of the plunger 21 on the small diameter portion 213 side. A plunger stopper 23 is disposed around the small diameter portion 213 of the plunger 21.

Next, the plunger stopper 23 and the state in which the plunger stopper 23 is disposed around the small diameter portion 213 of the plunger 21 will be described with reference to FIGS.
The plunger stopper 23 has a substantially concave cross section, and an insertion hole 239 for passing the small diameter portion 213 of the plunger 21 is opened at the center of the bottom surface portion 231 thereof. The end surface of the insertion hole 239 is opposed to the outer peripheral wall surface of the small diameter portion 213 with a predetermined gap. This gap is for communicating a variable volume chamber 30 and a cylindrical passage 31 described later.

  The surface of the bottom surface portion 231 of the plunger stopper 23 facing the pressurizing chamber 12 is opposed to the stepped portion 214 of the plunger 21 at the center side, and the cylinder hole forming portion 14 of the pump body 10 at the outer peripheral side thereof. The cylinder end 141 comes into contact. The surface of the plunger 21 that faces the stepped portion 214 serves as a stopper portion 232 for the stepped portion 214 of the plunger 21.

  The substantially concave outer wall portion 233 of the plunger stopper 23 is bent toward the center, and the bent portion 234 is engaged with the outer recess 15 of the cylinder hole forming portion 14. In addition, the substantially concave outer wall portion 233 of the plunger stopper 23 is formed with notches 235 at four locations, and the outer wall portion 233 including the bent portion 234 is separated into four. For this reason, the outer wall part 233 separated into four parts is given a degree of freedom of deformation, and the bent part 234 of the outer wall part 233 can be locked to the outer recess 15, or the locking can be released and removed. It is possible to do.

  In this way, the plunger stopper 23 is fixed to the pump body 10 by detachably engaging the bent portion 234 with the outer recess 15 of the cylinder hole forming portion 14, and abuts against the cylinder end portion 141 of the cylinder hole forming portion 14. The stopper portion 232 is made to be opposed to the stepped portion 214 of the plunger 21 at the position. For this reason, when the plunger 21 moves in the cylinder hole 11, the movement of the plunger 21 is restricted by the stepped portion 214 coming into contact with the stopper portion 232 of the plunger stopper 23. Even when the stepped portion 214 of the plunger 21 abuts against the stopper portion 232, the sliding surface of the large diameter portion 211 is in a state where all of the sliding surface is in contact with the inner wall surface of the cylinder hole 11, and protrudes from the cylinder hole 11. Will not be exposed.

  A fuel seal member 24 is mounted around the small diameter portion 213 around the small diameter portion 213 closer to the spring seat 27 than the plunger stopper 23. The fuel seal member 24 includes an inner peripheral Teflon (registered trademark) ring 241 and an outer peripheral O ring 242 (see FIG. 5 of the third embodiment) that are slidably in contact with the outer peripheral surface of the small diameter portion 213. Thus, the thickness of the fuel oil film around the small-diameter portion 213 is regulated, and the leakage of fuel to the engine due to the sliding of the plunger 21 is suppressed.

  A seal element 25 is attached around the small diameter portion 213. The seal element 25 has a substantially annular shape, and a part of the seal element 25 comes into contact with an end portion on the pressurizing chamber 12 side, an end portion on the spring seat 27 side, and an end portion on the outer peripheral side of the fuel seal member 24. ing. The other part of the seal element 25 is fitted into a substantially annular recess 13 formed in the pump body 10 and is fixed by welding, for example. Thus, the seal element 25 serves as a holder for fixing the fuel seal member 24.

  An oil seal 26 is attached to the end of the seal element 25 on the spring seat 27 side so as to surround the small diameter portion 213. The oil seal 26 is slidably in contact with the outer peripheral surface of the small-diameter portion 213, regulates the thickness of the oil film around the small-diameter portion 213, and suppresses oil leakage due to sliding of the plunger 21. It is.

  A spring seat 27 is coupled to the lower portion of the plunger 21. One end of a plunger spring 28 is locked to the spring seat 27. The other end of the plunger spring 28 is locked to a predetermined end surface of the seal element 25 fixed to the pump body 10. That is, the seal element 25 also functions as a locking member for the plunger spring 28.

  Plunger springs 28 having both ends locked to the seal element 25 and the spring seat 27 function as a return spring for the plunger 21 and urge the plunger 21 against a tappet (not shown). The plunger 21 reciprocates in the axial direction in the cylinder hole 11 by contacting the cam of the camshaft via the tappet by the return spring function of the plunger spring 28. By the reciprocating movement of the plunger 21, the volume of the pressurizing chamber 12 is changed, so that fuel is sucked and pressurized.

The variable volume chamber 30 is formed by the substantially annular space surrounded by the outer wall surface of the small diameter portion 213, the stepped portion 214 of the plunger 21 and the inner wall surface of the cylinder hole 11 (see the broken line in FIG. 2). That is, the variable volume chamber 30 is formed by surrounding the small diameter portion 213 in a substantially annular shape. As the plunger 21 reciprocates, the variable volume chamber 30 changes its volume by multiplying the cross-sectional area difference between the large diameter portion 211 and the small diameter portion 213 by the movement distance of the plunger 21.
In addition, a cylindrical passage 31 and an annular passage 32 that are in communication with each other are formed between the seal element 25 and the pump body 10. In addition, a return passage 33 communicating with the annular passage 32 is formed in the pump body 10. The variable volume chamber 30 communicates with the damper chamber 40 via the cylindrical passage 31, the annular passage 32, and the return passage 33.

(B) The damper chamber 40 will be described.
The damper chamber 40 includes a recess 41, a cover 42, a damper unit 43, and the like.
The pump body 10 is provided with a recess 41 that is recessed toward the cylinder hole 11 on the opposite side of the cylinder hole 11. The concave portion 41 is covered with a bottomed cylindrical cover 42 for blocking the inside from outside air.

A damper unit 43 is disposed in the damper chamber 40. The damper unit 43 includes a pulsation damper 44 formed by joining two metal diaphragms 441 and 442, a bottom support 45 disposed at the bottom of the recess 41, and a lid support provided on the cover 42 side. 46.
In the pulsation damper 44, a gas having a predetermined pressure is sealed inside two metal diaphragms 441 and 442. The two metal diaphragms 441 and 442 are elastically deformed according to the pressure change in the damper chamber 40, thereby reducing the fuel pressure pulsation in the damper chamber 40.

A recess 47 is formed at the bottom of the recess 41 of the damper chamber 40 so as to match the bottom support 45. The bottom support portion 45 is positioned by the recess 47. In addition, although not shown in the figure, an opening of a fuel inlet (inlet) is formed in the recess 47, so that fuel from the low-pressure pump is supplied to a radially inner region of the bottom support 45. . That is, the fuel in the fuel tank is supplied to the damper chamber 40 through the fuel inlet.
A wave spring 48 is disposed above the lid side support 46. Thereby, the wave spring 48 presses the lid-side support portion 46 toward the bottom-side support portion 45 with the cover 42 attached to the pump body 10. As a result, the pulsation damper 44 is clamped and fixed at the periphery by the lid-side support portion 46 and the bottom-side support portion 45 with an equal force in the circumferential direction.

(C) The suction valve unit 50 will be described.
The suction valve unit 50 includes a supply passage 52, a valve body 53, a seat portion 54, a suction valve 55, and the like.
The pump body 10 is provided with a cylindrical portion 51 substantially perpendicular to the central axis of the cylinder hole 11, and the inside of the cylindrical portion 51 is a fuel supply passage 52. Further, a valve body 53 is accommodated inside the cylindrical portion 51 and is fixed by a locking member. A seat portion 54 having a concave tapered circumferential surface is formed inside the valve body 53, and a suction valve 55 is disposed opposite to the seat portion 54. The suction valve 55 is guided by an inner wall of a hole provided at the bottom of the valve body 53 and reciprocates. The suction valve 55 is separated from the seat portion 54 to open the supply passage 52. When the suction valve 55 is seated on the seat portion 54, the supply passage 52 is closed.

A stopper 56 is fixed to the inner wall of the valve body 53, and this stopper 56 restricts the movement of the intake valve 55 in the valve opening direction (right direction in FIG. 1). A first spring 57 is provided between the inside of the stopper 56 and the end face of the suction valve 55. The first spring 57 attaches the suction valve 55 in the valve closing direction (left direction in FIG. 1). Rush.
The stopper 56 is formed with a plurality of inclined passages 58 that are inclined with respect to the axis of the stopper 56 in the circumferential direction. The fuel supplied through the supply passage 52 is sucked into the pressurizing chamber 12 through the inclined passage 58. The supply passage 52 communicates with the damper chamber 40 via the pressurization side passage 59.

(D) The electromagnetic drive unit 60 will be described.
The electromagnetic drive unit 60 includes a connector 61, a fixed core 62, a movable core 63, a flange 64, and the like.
The connector 61 includes a coil 611 and a terminal 612, and generates a magnetic field when the coil 611 is energized through the terminal 612. The fixed core 62 is made of a magnetic material and is accommodated inside the coil 611. The movable core 63 is made of a magnetic material and is disposed to face the fixed core 62. The movable core 63 is accommodated inside the flange 64 so as to be capable of reciprocating in the axial direction.

The flange 64 is made of a magnetic material and is attached to the cylinder portion 51 of the pump body 10. The flange 64 holds the connector 61 and the like on the pump body 10 and closes the end of the cylindrical portion 51. A cylindrical guide cylinder 65 is attached to the inner wall of the hole provided in the center of the flange 64. The cylindrical member 66 made of a nonmagnetic material prevents a magnetic short circuit between the fixed core 62 and the flange 64.
The needle 67 is formed in a substantially cylindrical shape, and is reciprocated while being guided by the inner wall of the guide cylinder 65. One end of the needle 67 is fixed to the movable core 63, and the other end can be brought into contact with the end surface of the suction valve 55 on the electromagnetic drive unit 60 side.

A second spring 68 is provided between the fixed core 62 and the movable core 63. The second spring 68 biases the movable core 63 in the valve opening direction with a force stronger than the force that the first spring 57 biases the suction valve 55 in the valve closing direction.
When the coil 611 is not energized, the movable core 63 and the fixed core 62 are separated from each other by the elastic force of the second spring 68. As a result, the needle 67 integral with the movable core 63 moves to the suction valve 55 side, and the suction valve 55 is opened when the end surface of the needle 67 presses the suction valve 55.

(E) The discharge valve unit 70 will be described.
The discharge valve unit 70 includes a discharge passage 71, a discharge valve device 80, and the like.
A discharge passage 71 is formed in the pump body 10 substantially perpendicularly to the central axis of the cylinder hole 11. The discharge passage 71 communicates with the pressurizing chamber 12 on the one hand and communicates with the fuel outlet 72 on the other hand. A discharge valve device 80 is assembled in the discharge passage 71.

The discharge valve device 80 includes a discharge valve member 82, a spring 83, an adjusting pipe 84, and the like.
The discharge valve member 82 is accommodated relative to the valve seat 85 of the pump body 10.

A spring 83 as an urging member is accommodated on the fuel outlet 72 side of the discharge valve member 82. One end of the spring 83 is in contact with the second end surface of the discharge valve member 82. A cylindrical adjusting pipe 84 is accommodated on the fuel outlet 72 side of the spring 83. The adjusting pipe 84 is engaged with the other end of the spring 83 as a support member.
Thus, the discharge valve member 82, the spring 83, and the adjusting pipe 84 are provided, and the discharge valve member 82 is biased by the biasing force of the spring 83 whose end is locked to the adjusting pipe 84. 80 is assembled to the discharge valve portion 70.

Thus, the discharge valve apparatus 80 assembled | attached to the discharge valve part 70 operate | moves as follows.
As the plunger 21 rises in the cylinder hole 11, the fuel pressure in the pressurizing chamber 12 rises. The force received by the discharge valve member 82 from the fuel on the pressure chamber 12 side (upstream side) of the discharge valve member 82 of the discharge valve device 80 is the elastic force of the spring 83 and the fuel outlet 72 side (from the discharge valve member 82). When greater than the sum of the forces received from the fuel on the downstream side, the discharge valve member 82 separates from the valve seat 85 of the pump body 10. That is, the discharge valve device 80 is opened. As a result, the high-pressure fuel pressurized in the pressurizing chamber 12 is discharged to the fuel outlet 72 through the discharge passage 71.

On the other hand, as the plunger 21 descends in the cylinder hole 11, the fuel pressure in the pressurizing chamber 12 decreases. When the force received by the discharge valve member 82 from the fuel on the upstream side is equal to or smaller than the sum of the elastic force of the spring 83 and the force received from the fuel on the downstream side, the discharge valve member 82 becomes the valve seat 85 of the pump body 10. Sit on. That is, the discharge valve device 80 is closed. This prevents fuel downstream from the discharge valve member 82 from flowing back into the upstream pressurizing chamber 12.
In this way, the discharge valve device 80 assembled to the discharge valve portion 70 functions as a check valve for high-pressure fuel discharged from the pressurizing chamber 12 toward the fuel outlet 72.

Next, the operation of the high-pressure pump 1 will be described.
(1) Suction stroke When the plunger 21 descends from the top dead center toward the bottom dead center in the cylinder hole 11 due to the rotation of the camshaft, the volume of the pressurizing chamber 12 increases and the fuel in the pressurizing chamber 12 flows. Depressurized. At this time, in the discharge valve portion 70, the discharge valve member 82 of the discharge valve device 80 is seated on the valve seat 85 and closes the discharge passage 71. Further, in the suction valve section 50, the suction valve 55 moves to the right in FIG. 1 against the urging force of the first spring 57 due to the pressure difference between the pressurizing chamber 12 and the supply passage 52, and the valve is opened. It becomes a state. At this time, since the energization of the coil 611 of the electromagnetic drive unit 60 is stopped, the movable core 63 and the needle 67 integral with the movable core 63 move to the right in FIG. 1 by the urging force of the second spring 68. . Accordingly, the needle 67 and the suction valve 55 come into contact with each other, and the suction valve 55 maintains the open state. As a result, fuel is sucked into the pressurizing chamber 12 from the supply passage 52.

In the suction stroke, the volume of the variable volume chamber 30 decreases due to the lowering of the plunger 21. Accordingly, the fuel in the variable volume chamber 30 is sent out to the damper chamber 40 via the cylindrical passage 31, the annular passage 32, and the return passage 33.
Here, the cross-sectional area ratio between the large diameter portion 211 and the variable volume chamber 30 is approximately 1: 0.6. Therefore, the ratio of the increase in the volume of the pressurizing chamber 12 to the decrease in the volume of the variable volume chamber 30 is also 1: 0.6. For this reason, about 60% of the fuel sucked into the pressurizing chamber 12 is supplied from the variable volume chamber 30, and the remaining about 40% is sucked from the fuel inlet. Thereby, the fuel suction efficiency into the pressurizing chamber 12 is improved.

(2) Metering stroke When the plunger 21 moves up from the bottom dead center toward the top dead center in the cylinder hole 11 due to the rotation of the camshaft, the volume of the pressurizing chamber 12 decreases. At this time, since energization to the coil 611 is stopped until a predetermined time, the needle 67 and the suction valve 55 are positioned in the right direction in FIG. 1 by the urging force of the second spring 68. As a result, the supply passage 52 is kept open. For this reason, the low-pressure fuel once sucked into the pressurizing chamber 12 is returned to the supply passage 52. Therefore, the pressure in the pressurizing chamber 12 does not increase.

In the metering stroke, the volume of the variable volume chamber 30 increases as the plunger 21 rises. Therefore, the fuel in the damper chamber 40 flows into the variable volume chamber 30 via the return passage 33, the annular passage 32, and the cylindrical passage 31.
At this time, about 60% of the volume of the low-pressure fuel discharged from the pressurizing chamber 12 to the damper chamber 40 is sucked into the variable volume chamber 30 from the damper chamber 40. This reduces about 60% of the fuel pressure pulsation.

(3) Pressurization stroke The coil 611 is energized at a predetermined time while the plunger 21 rises in the cylinder hole 11 from the bottom dead center toward the top dead center. Then, a magnetic attractive force is generated between the fixed core 62 and the movable core 63 by the magnetic field generated in the coil 611. When this magnetic attractive force becomes larger than the difference between the elastic force of the second spring 68 and the elastic force of the first spring 57, the movable core 63 and the needle 67 move to the fixed core 62 side (left direction in FIG. 1). Thereby, the pressing force of the needle 67 against the suction valve 55 is released. The suction valve 55 moves to the seat portion 54 side by the elastic force of the first spring 57 and the force generated by the flow of low-pressure fuel discharged from the pressurizing chamber 12 to the damper chamber 40 side. Accordingly, the suction valve 55 is seated on the seat portion 54 and the supply passage 52 is closed.

From when the intake valve 55 is seated on the seat portion 54, the fuel pressure in the pressurizing chamber 12 increases as the plunger 21 rises toward the top dead center. In the discharge valve portion 70, the force that the upstream fuel pressure acts on the discharge valve member 82 of the discharge valve device 80 is the force that the downstream fuel pressure acts on the discharge valve member 82 and the spring 83. When it becomes larger than the sum of the urging forces, the discharge valve member 82 opens. As a result, the high-pressure fuel pressurized in the pressurizing chamber 12 is discharged from the fuel outlet 72 via the discharge passage 71.
Note that energization of the coil 611 is stopped during the pressurization stroke. Since the force that the fuel pressure in the pressurizing chamber 12 acts on the suction valve 55 is larger than the urging force of the second spring 68, the suction valve 55 maintains the closed state.

The high-pressure pump 1 repeats (1) the intake stroke, (2) the metering stroke, and (3) the pressurization stroke to pressurize and discharge a necessary amount of fuel to the internal combustion engine.
If the timing of energizing the coil 611 is advanced, the time of the metering stroke is shortened and the time of the pressurizing stroke is lengthened. As a result, the amount of fuel returned from the pressurizing chamber 12 to the supply passage 52 decreases, and the amount of fuel discharged from the discharge passage 71 increases. On the other hand, if the timing of energizing the coil 611 is delayed, the time of the metering stroke becomes longer and the time of the discharge stroke becomes shorter. Thereby, the fuel returned from the pressurizing chamber 12 to the supply passage 52 increases, and the fuel discharged from the discharge passage 71 decreases.
Thus, by controlling the timing of energizing the coil 611, the amount of fuel discharged from the high-pressure pump 1 is controlled to the amount required by the internal combustion engine.

Next, the effect of this embodiment is demonstrated.
In this embodiment, the plunger stopper 23 is fixed to the pump body 10 by releasably engaging the bent portion 234 with the outer recess 15 of the cylinder hole forming portion 14, while the stopper portion 232 is fixed to the step of the plunger 21. It is made to oppose with the attaching part 214. FIG.
For this reason, the stopper part 232 of the plunger stopper 23 not only fulfills the stopper function when the plunger 21 reciprocates in the cylinder hole 11 after the high pressure pump 1 is assembled. Even in the process of mounting the pump 1 on the engine, the stopper 21 prevents the plunger 21 from dropping from the cylinder hole 11.

  In addition, since the position of the stopper portion 232 of the plunger stopper 23 in the axial direction of the cylinder hole 11 is the same position as the cylinder end portion 141 of the cylinder hole forming portion 14, a step is formed by the movement of the plunger 21 in the cylinder hole 11. Even when the portion 214 abuts against the stopper portion 232, the sliding surface of the large diameter portion 211 is in a state where the entire sliding surface is in contact with the inner wall surface of the cylinder hole 11 and does not protrude from the cylinder hole 11. Therefore, the sliding surface of the plunger 21 is kept in a protected state so as not to cause dents or foreign matter adhesion.

  That is, during the operation of the high-pressure pump 1, it is possible to protect the plunger sliding surface from dents and foreign matters, and to prevent poor plunger sliding. Further, even in the assembly process of the high-pressure pump 1 and the engine mounting process, the plunger 21 is prevented from dropping from the cylinder hole 11 in a state where the sliding surface of the plunger 21 is protected so as not to cause dents or foreign matters. be able to.

(Modification of the first embodiment)
In the above configuration, the position of the stopper portion 232 of the plunger stopper 23 in the axial direction of the cylinder hole 11 is the same as the cylinder end portion 141 of the cylinder hole forming portion 14, but the position of the stopper portion 232 of the plunger stopper 23 is Even when the cylinder hole forming portion 14 is closer to the pressurizing chamber 12 side than the cylinder end portion 141, the same effect can be obtained.
For example, as shown in FIG. 3, the plunger stopper 23 </ b> A of the modified example forms a convex portion protruding toward the pressurizing chamber 12 near the center of the bottom surface portion 231, and the stepped portion 214 of the plunger 21 of the convex portion is formed. The opposing surfaces form a stopper portion 232a. Therefore, the stopper portion 232a is positioned closer to the pressurizing chamber 12 side than the surface that contacts the cylinder end portion 141 of the cylinder hole forming portion 14 on the outer peripheral side of the bottom surface portion 231.

(Reference form)
FIG. 4A shows a state where the plunger stopper is attached to the pump body of the high-pressure pump according to the reference embodiment, and FIG. 4B shows the plunger stopper.
In the following embodiments and reference embodiments, substantially the same components as those of the first embodiment are denoted by the same reference numerals and description thereof is omitted. In the present specification, there is no “second embodiment”.
An inner recess 16 is formed in a circumferential shape on the inner wall surface of the cylinder hole 11 of the pump body 10 of the high-pressure pump 2 according to the present embodiment, that is, the inner wall surface 143 of the cylinder hole forming portion 14.

The plunger stopper 29 is a string-like member having a substantially circular cross section and having a predetermined flexibility, and is engaged in the inner recess 16 of the circumference. A part of the plunger stopper 29 engaged in the inner recess 16 protrudes from the inner recess 16 toward the center axis of the cylinder hole 11. The circumferential surface of the plunger stopper 29 protruding from the inner recess 16 and facing the pressurizing chamber 12 side and facing the stepped portion 214 of the plunger 21 is a stepped portion of the plunger 21. It becomes a stopper part 292 for 214.
Since the plunger stopper 29 is a string-like member having a predetermined flexibility, the plunger stopper 29 can be deformed. Therefore, the plunger stopper 29 can be engaged in the inner recess 16 or can be removed after being disengaged. It is possible.

Next, the effect of this reference form is demonstrated.
In the present embodiment, the plunger stopper 29 is detachably engaged with the inner recess 16 and fixed to the pump body 10, while the cylinder end portion 141 of the cylinder hole forming portion 14 is closer to the pressurizing chamber 12 side. , The stopper portion 292 is opposed to the stepped portion 214 of the plunger 21.

For this reason, as in the case of the first embodiment, even when the stepped portion 214 comes into contact with the stopper portion 292 due to the movement of the plunger 21 in the cylinder hole 11, the sliding surface of the large diameter portion 211 is entirely. It will be in the state which contacted the inner wall face of the cylinder hole 11, and does not protrude from the cylinder hole 11, and will not be in an exposure state.
Thus, in a state where the sliding surface of the plunger 21 is protected so as not to cause dents or adhesion of foreign matter, it is possible to prevent the sliding failure of the plunger 21 during the operation of the high-pressure pump 2. The plunger 21 can be prevented from dropping from the cylinder hole 11 during the assembly process or the engine mounting process.

(Third embodiment)
FIG. 5 shows an enlarged view of the plunger portion of the high-pressure pump 3 according to the third embodiment of the present invention. Moreover, the 1st ring and 2nd ring which comprise the plunger stopper by the basic example of 3rd Embodiment, and the said plunger stopper are shown to FIG. 6, FIG.
As shown in FIG. 5, the plunger stopper 34 of the third embodiment is fixed to the outer wall surface 142 of the cylinder hole forming portion 14 in the same manner as the plunger stopper 23 of the first embodiment. However, in the plunger stopper 23 of the first embodiment, the bent portion 234 is locked to the outer recess 15 of the outer wall surface 142 and fixed to the outer wall surface 142, whereas the plunger stopper 34 of the third embodiment has a plurality of plunger stoppers 34. The engaging portion 351 is pressed against the outer wall surface 142 of the cylinder hole forming portion 14 by the elastic force in the radially inward direction and fixed so as to hold the outer wall surface 142.

The plunger stopper 34 includes a first ring 35 and a second ring 36 shown in FIG. In the present embodiment, both the first ring 35 and the second ring 36 are formed by pressing a metal such as stainless steel.
The first ring 35 is formed of a plate material such as a spring steel plate having a relatively thin plate thickness, and an insertion hole 359 through which the small diameter portion 213 of the plunger 21 can be inserted is formed around the axis Z in the approximate center of the main body 350. The

In addition, three engaging portions 351 are provided on the outer edge of the main body 350 at substantially equal intervals in the circumferential direction. The engaging portion 351 is bent in a direction substantially orthogonal to the base surface 358 of the main body 350 (upward in the drawing). More specifically, the engaging portions are arranged such that the virtual diameter by the fitting portion 352 formed on the inner diameter surface near the upper end portions of the three engaging portions 351 is slightly smaller than the diameter of the outer wall surface 142 of the cylinder hole forming portion 14. 351 is bent with a slight inclination in the radial direction from the direction orthogonal to the base surface 358. Thereby, when the plunger stopper 34 is attached to the cylinder hole formation part 14, the three engaging parts 351 have the elastic force to radial direction.
If the three engaging portions 351 are evenly arranged in the circumferential direction, the minimum number can be engaged with a good balance. However, in other embodiments, the number and arrangement of the engaging portions are not limited to this.

  A protrusion 354 that protrudes in the radially inward direction is formed at an intermediate portion in the bending direction of the engaging portion 351. When the first ring 35 and the second ring 36 are combined, the protrusion 354 engages with the main body 360 of the second ring 36 to prevent the first ring 35 and the second ring 36 from being detached. At this time, the root portion 353 of the engaging portion 351 faces the outer wall surface of the main body 360 of the second ring 36.

  The second ring 36 is formed of a relatively thick plate material. An insertion hole 369 that corresponds to the insertion hole 359 of the first ring 35 and through which the small diameter portion 213 of the plunger 21 can be inserted is formed at the approximate center of the main body 360. When the first ring 35 and the second ring 36 are combined, the lower surface 362 of the main body 360 of the second ring 36 contacts the base surface 358 of the first ring 35. Since the main body 360 of the second ring 36 is relatively thick, the rigidity of the plunger stopper 34 can be increased and deformation due to fuel pressure can be prevented.

  Three cutout portions 367 corresponding to the positions of the engaging portions 351 of the first ring 35 are provided on the outer edge of the main body 360. When the first ring 35 and the second ring 36 are combined, the engagement portion 351 is disposed inside the outer diameter of the second ring 36 by the engagement portion 351 engaging with the notch portion 367. . For this reason, the outer diameter of the second ring 36 can be made to correspond to the inner diameter of the seal element 25, and the space can be used effectively (see FIG. 5). Further, the first ring 35 and the second ring 36 are prevented from rotating.

Further, the main body 360 is provided with three convex portions 363 projecting upward in the figure between the circumferential notches 367. The heights of the upper surfaces 364 of the three convex portions 363 are substantially the same, and the plunger stopper 34 is positioned in the axial direction with respect to the cylinder hole forming portion 14 by the upper surface 364 being abutted against the cylinder end portion 141.
A space between the convex portions 363 in the circumferential direction forms a communication path 366. The height of the communication path 366 corresponds to a difference in height between the upper surface 361 of the main body 360 and the upper surface 364 of the convex portion 363. The communication passage 366 communicates the variable volume chamber 30 in the radially inner direction of the plunger stopper 34 and the cylindrical passage 31 in the radially outward direction.

  The inner diameter of the virtual circle connecting the inner wall 365 of the convex portion 363 is slightly larger than the diameter of the large diameter portion 211 of the plunger 21, and can guide the large diameter portion 211 of the plunger 21. An annular stopper portion 368 is formed between a virtual circle connecting the inner walls 365 of the three convex portions 363 and the insertion hole 369. The stopper portion 368 is formed as a step on the upper surface 361 of the main body 360 in the lower part of the drawing, that is, on the side opposite to the convex portion 363. When the plunger 21 is lowered, the stopper portion 368 comes into contact with the stepped portion 214 and restricts the movement of the plunger 21.

  For this reason, the stopper portion 368 of the plunger stopper 34 not only fulfills the stopper function when the plunger 21 reciprocates in the cylinder hole 11 after the high pressure pump 3 is assembled, but also the process of assembling the high pressure pump 3 and the assembled high pressure pump. Even in the process of mounting the pump 3 on the engine, the stopper 21 prevents the plunger 21 from dropping from the cylinder hole 11.

  In the present embodiment, when the plunger 21 is lowered, the fuel contacts the portion corresponding to the circumferential communication passage 366 of the large diameter portion 211 via the communication passage 366, so that a part of the sliding portion is exposed. It seems to be. However, at least during the reciprocating movement of the plunger 21 in the cylinder hole 11 during the operation after the high pressure pump 3 is assembled, or when the plunger 21 is dropped from the cylinder hole 11 in the assembly process of the high pressure pump 3 or the engine mounting process. When preventing, the sliding surface of the plunger 21 is maintained in a protected state so as not to cause dents or the like.

  In the present embodiment, the plunger stopper 34 is configured by combining the first ring 35 having the engaging portion 351 and the second ring 36 that shakes the convex portion 363. Thereby, the 1st ring 35 in which elasticity is requested | required and the 2nd ring 36 in which rigidity is requested | required can each be formed with the board | plate thickness material suitable for press work. Therefore, the manufacturing efficiency can be improved and the total manufacturing cost can be reduced.

(Modification of the third embodiment)
First to fifth modifications of the third embodiment will be described with reference to FIGS. These modified examples are different from the above basic example in the configuration in which the first ring and the second ring are engaged and separated. Specifically, an auxiliary claw or the like is employed in the first ring in place of the protrusion 354 of the basic example. In the first to third embodiments, the second ring 36 is substantially the same as the second ring 36 of the basic example.

  As shown in FIG. 8, in the plunger stopper 34A of the first modification of the third embodiment, a window portion 355a is formed in the engaging portion 351a of the first ring 35A, and an auxiliary claw 356a is provided in the window portion 355a. . The auxiliary claw 356a is bent upward from the base part 353 side of the engaging part 351a independently of the main claw part forming the fitting part 352. The auxiliary claw 356a has an elastic force in the radially inward direction, and presses the upper surface 361 of the main body 360 or the side surface of the notch 367 of the second ring 36 to prevent the second ring 36 from being detached from the first ring 35A.

  As shown in FIG. 9, in the plunger stopper 34B of the second modification of the third embodiment, a window portion 355b is formed in the engaging portion 351b of the first ring 35B, and an auxiliary claw 356b is provided in the window portion 355b. . The auxiliary claw 356b is bent diagonally downward from the upper end of the window portion 355b, independently of the main claw portion that forms the fitting portion 352. The auxiliary claw 356b presses the upper surface 361 of the main body 360 of the second ring 36 and prevents the second ring 36 from being detached from the first ring 35B.

  As shown in FIG. 10, in the plunger stopper 34C of the third modification of the third embodiment, a window portion 355c is formed in the engaging portion 351c of the first ring 35C, and an auxiliary claw 356c is provided in the window portion 355c. . The auxiliary claw 356c is bent into a hook shape upward from the root portion 353 side of the engaging portion 351c and then radially inward, independently of the main claw portion forming the fit portion 352. The auxiliary claw 356c presses the upper surface 361 of the main body 360 of the second ring 36 and prevents the second ring 36 from being detached from the first ring 35C.

  Next, as shown in FIG. 11, the plunger stopper 34D of the fourth modification of the third embodiment has an auxiliary claw 357d different from the engaging portion 351d of the first ring 35D in the circumferential direction of the engaging portion 351d. Adjacent to each other. The auxiliary claw 357d is bent upward from the base surface 358 of the main body 350. The second ring 36D is formed so that the length of the notch 367d in the circumferential direction is longer than the second ring 36 of the basic example. The auxiliary claw 357d has an elastic force in the radially inward direction, and presses the upper surface 361 of the main body 360 of the second ring 36D or the side surface of the notch 367d to prevent the second ring 36D from being detached from the first ring 35D.

  As shown in FIG. 12, the plunger stopper 34E of the sixth modification of the third embodiment has an auxiliary claw 357e different from the engaging portion 351e of the first ring 35E, in the circumferential direction between the engaging portions 351e. Between. The auxiliary claw 357 e is bent upward from the base surface 358 of the main body 350. Similar to the second ring 36 of the basic example, the second ring 36E is provided with three notches 367 for the engaging portion 351e between the convex portions 363e of the main body 360, and the auxiliary claw is provided on the convex portion 363e. Three notches 367e for 357e are provided. The auxiliary claw 357e has an elastic force toward the radially inward direction, presses the side surface of the notch 367e of the second ring 36E, and prevents the first claw 357e from being detached from the first ring 35E.

(Fourth embodiment)
A plunger stopper according to a fourth embodiment of the present invention is shown in FIG. The plunger stopper 37 of the basic example of the fourth embodiment is provided with an outer recess in the cylinder hole forming portion 14 by the elastic force in the radially inward direction of the plurality of engaging portions 371, like the plunger stopper 34 of the third embodiment. It is fixed so that the outer wall surface 142 may be held.

As shown in FIG. 13, the plunger stopper 37 of the fourth embodiment is constituted by one part by pressing a metal such as stainless steel.
The plunger stopper 37 is formed of a spring steel plate or the like having a relatively thin plate thickness corresponding to the material of the first ring 35 of the third embodiment, and is inserted through the small diameter portion 213 of the plunger 21 at substantially the center of the main body 370. A hole 379 is formed about the axis Z.

  In addition, three engagement portions 371 are provided at substantially equal intervals in the circumferential direction on the outer edge of the main body 370, and the engagement portions 371 are bent in a direction substantially orthogonal to the base surface 377 of the main body 370 (upward in the drawing). As in the third embodiment, the fitting portion 372 formed on the radially inner surface near the upper end of the engaging portion 371 contacts the outer wall surface 142 of the cylinder hole forming portion 14.

On the other hand, unlike the third embodiment, in the plunger stopper 37, the three convex portions 373 are formed integrally with the main body 370 by bending. The heights of the upper surfaces 374 of the three convex portions 373 are substantially the same, and the plunger stopper 37 is positioned in the axial direction with respect to the cylinder hole forming portion 14 by the upper surface 374 being abutted against the cylinder end portion 141.
A space between the convex portions 373 in the circumferential direction forms a communication path 376. The height of the communication path 376 corresponds to a difference in height between the base surface 377 of the main body 370 and the upper surface 374 of the convex portion 373.
In particular, in the basic example shown in FIG. 13, the base surface 377 on the inner side of the inner wall 375 of the convex portion 373 also serves as a stopper portion.

  Although the fourth embodiment is disadvantageous in that the rigidity of the convex portion and the stopper portion is increased as compared with the third embodiment in which the plunger stopper 34 is configured by combining two components, the plunger stopper 37 is configured by one component. Therefore, the number of parts can be reduced. Therefore, the manufacturing cost can be reduced.

(Modification of the fourth embodiment)
The plunger stopper 37A of the modified example of the fourth embodiment shown in FIG. 14 differs from the basic example only in the configuration of the convex portion 373a. That is, the convex portion 373a is bent so that the inner wall 375 is further folded, so that the stopper portion 378 is formed.
Thereby, the rigidity of the stopper part 378 can be improved compared with the basic example.

(Fifth embodiment)
FIG. 15 shows a state where a plunger stopper is attached to the plunger portion of the high-pressure pump according to the fifth embodiment of the present invention.
A plunger portion 20A of the high-pressure pump 5 according to the present embodiment will be described with reference to FIG. In addition, since parts other than the plunger part 20 have the same configuration as the high-pressure pump 1 shown in FIG. 1 of the first embodiment, the description thereof is omitted.
The plunger portion 20A includes a plunger 21A, a plunger stopper 38, a fuel seal member 24, a seal element 25A, a plunger spring 28, a variable volume chamber 30, and the like.

  The plunger 21A has a large-diameter portion 211a whose one end faces the pressurizing chamber 12 and slides along the inner wall constituting the cylinder hole 11, and has a smaller outer diameter than the large-diameter portion 211a. An intermediate diameter portion 212a extending from 211a to the opposite side to the pressurizing chamber 12 side, and an outer diameter smaller than the intermediate diameter portion 212a, and a small diameter portion 213a extending from the intermediate diameter portion 212a to the opposite side to the pressurizing chamber 12 side. And have. The large diameter portion 211a, the medium diameter portion 212a, and the small diameter portion 213a are coaxial, and a first stepped portion 214a is formed at the boundary between the large diameter portion 211a and the medium diameter portion 212a. A second stepped portion 214b is formed at the boundary between 212a and the small diameter portion 213a.

  A fuel seal member 24 is mounted around the middle diameter portion 212a of the plunger 21A to suppress fuel leakage to the engine due to sliding of the plunger 21A. Similarly, a seal element 25A is mounted around the small diameter portion 213a. The seal element 25A has a substantially annular shape as a whole, and a part thereof is in contact with the end of the fuel seal member 24 on the pressurizing chamber 12 side and the end of the outer peripheral side. The other part of the seal element 25A is fitted into a substantially annular recess 13 formed in the pump body 10, and is fixed by welding, for example.

A plunger stopper 38 is arranged in a substantially annular shape around the middle diameter portion 212a and the small diameter portion 213a opposite to the pressurizing chamber 12 from the fuel seal member 24. An end surface facing the second stepped portion 214b of the plunger 21A is formed on the inner wall surface side of the plunger stopper 38, and this end surface serves as a stopper portion 382 for the second stepped portion 214b of the plunger 21A.
Here, the distance L1 between the stopper portion 382 of the plunger stopper 38 and the cylinder end portion 141 of the cylinder hole forming portion 14 is the axial length L2 of the intermediate diameter portion 212a of the plunger 21A, that is, the first stage of the plunger 21A. This is equal to the distance L2 between the attached portion 214a and the second stepped portion 214b.

  The outer peripheral wall surface of the plunger stopper 38 is connected to the seal element 25A. That is, the plunger stopper 38 is fixed to the pump body 10 via the seal element 25A. The end portion of the plunger stopper 38 on the pressurizing chamber 12 side is in contact with the end portion 22 of the fuel seal member 24 opposite to the pressurizing chamber 12. Thus, the plunger stopper 38 also functions as a holder that fixes the fuel seal member 24 integrally with the seal element 25A.

Next, the effect of this embodiment is demonstrated.
In the present embodiment, the plunger stopper 38 is fixed to the pump body 10 via the seal element 25A, and the stopper portion 382 is opposed to the second stepped portion 214b of the plunger 21A. Moreover, the distance L1 between the stopper portion 382 of the plunger stopper 38 and the cylinder end portion 141 of the cylinder hole forming portion 14 is the distance L2 between the first stepped portion 214a and the second stepped portion 214b, that is, the medium diameter of the plunger 21A. It is equal to the axial length L2 of the portion 212a.

  Therefore, as in the case of the first embodiment, even when the second stepped portion 214b comes into contact with the stopper portion 382 due to the movement of the plunger 21A in the cylinder hole 11, the sliding surface of the large diameter portion 211a The whole is in contact with the inner wall surface of the cylinder hole 11 and does not protrude from the cylinder hole 11 and is not exposed. In this way, in a state where the sliding surface of the plunger 21A is protected so as not to cause dents or adhesion of foreign matters, the sliding failure of the plunger 21A during the operation of the high pressure pump 2, the assembly process of the high pressure pump 2, and the engine mounting It is possible to prevent the plunger 21A from dropping from the cylinder hole 11 in the process.

  Further, since the fuel seal member 24 is interposed between the first stepped portion 214a of the plunger 21A and the stopper portion 382 of the plunger stopper 38, the stopper portion 382 is separated from the fuel region such as the variable volume chamber 30. Completely separated. For this reason, even if a small amount of foreign matter is generated when the first stepped portion 214a of the plunger 21A comes into contact with the stopper portion 382 of the plunger stopper 38, the foreign matter is formed between the sliding surface of the large-diameter portion 211a and the cylinder hole 11. Eliminates intrusion between the inner wall. Therefore, the sliding failure of the plunger 21A during the operation of the high-pressure pump 2 can be prevented.

(Sixth embodiment)
FIG. 16 shows a high-pressure pump according to a sixth embodiment of the present invention. First, a high-pressure pump 6 according to this embodiment will be described with reference to FIG.
The high pressure pump 6 is a separate cylinder type high pressure pump in which a cylinder hole is formed of a member different from the pump body 10. That is, the cylinder forming member 90 is a member that is connected to the pump body 10 but separate from the pump body 10. The cylinder forming member 90 is integrally formed with a cylindrical cylinder hole 91 and a pressurizing chamber 92 communicating with the cylinder hole 91.

An outer recess 93 is formed on the outer wall surface near the end of the cylinder forming member 90 opposite to the pressurizing chamber 92 in a circumferential shape. As in the case of the first embodiment, a plunger having substantially the same structure as the plunger stopper 23 of the first embodiment is provided near the end of the cylinder forming member 90 on the side opposite to the pressurizing chamber 92. A stopper 23 is attached.
That is, the bent portion 234 of the plunger stopper 23 is fixed to the pump body 10 by detachably engaging with the outer recess 93 of the cylinder forming member 90. In addition, the stopper portion 232 of the plunger stopper 23 is opposed to the stepped portion 214 of the plunger 21 at the position of the end of the cylinder forming member 90 opposite to the pressurizing chamber 92 side.

  For this reason, as in the case of the first embodiment, the plunger 21 moves in the cylinder hole 91, and even when the stepped portion 214 abuts against the stopper portion 232 of the plunger stopper 23, the sliding of the large diameter portion 211 is performed. The entire moving surface is in contact with the inner wall surface of the cylinder hole 91 and does not protrude from the cylinder hole 91 and is not exposed. In this way, the state in which the sliding surface of the plunger 21 is protected so as not to cause dents or adhesion of foreign matters is maintained.

Next, the effect of this embodiment is demonstrated.
Whereas the high-pressure pump 1 of the first embodiment uses a cylinder-integrated pump body, the high-pressure pump 6 of the present embodiment has a cylinder-separated pump in which the pump body 10 and the cylinder forming member 90 are separate bodies. The body is used. Further, the outer recess 15 in the first embodiment is formed on the wall surface on the recess 13 side of the cylinder hole forming portion 14 of the pump body 10, whereas the outer recess 93 is a cylinder forming member 90 in the present embodiment. It is different in that it is formed on the outer wall portion.

  However, in the present embodiment, despite the difference from the first embodiment, the position of the stopper portion 232 of the plunger stopper 23 in the axial direction of the cylinder hole 91 is the end of the cylinder forming member 90. By having the same position as the part, the same operational effects as in the case of the first embodiment are obtained. In other words, the plunger stopper 23 has versatility that it can be suitably used for both the high-pressure pump 1 using the cylinder-integrated pump body and the high-pressure pump 6 using the cylinder-separated pump body.

(Other embodiments)
In the third and fourth embodiments, the engaging portions 351, 371 and the like of the plunger stoppers 34, 37 have an elastic force in the radially inward direction, so that the outer recess 142 is formed on the outer wall surface 142 of the cylinder hole forming portion 14. Even if not formed, the outer wall surface 142 can be engaged by being pressed by the elastic force. However, an outer recess may be formed on the outer wall surface 142 of the cylinder hole forming portion 14, and the engaging portion may be engaged with the outer recess.

  In the fifth embodiment, the distance L1 between the stopper portion 382 of the plunger stopper 38 and the cylinder end portion 141 of the cylinder hole forming portion 14 is the distance L2 between the first stepped portion 214a and the second stepped portion 214b. That is, although it is equal to the axial length L2 of the middle diameter portion 212a of the plunger 21A, the same effects can be obtained even if the distance L1 is shorter than the length L2. In this case, it can be easily realized by changing the mounting position of the plunger stopper 38 or changing the shape of the plunger 21A.

  In the sixth embodiment, a case is described in which a plunger stopper having substantially the same structure as the plunger stopper 23 of the first embodiment is attached to a cylinder forming member 90 that is separate from the pump body 10. It is also possible to attach a plunger stopper having substantially the same structure as the plunger stoppers 34, 37, 38 of the third to fifth embodiments to the cylinder forming member 90.

1, 3, 5, 6 ... high pressure pump 10 ... pump body (cylinder forming member)
DESCRIPTION OF SYMBOLS 11, 91 ... Cylinder hole 12, 92 ... Pressurizing chamber 13 ... Recessed part 14 ... Cylinder hole formation part 141 ... Cylinder edge part 142 ... Outer wall surface 15, 93 ... Outer Recess (first and sixth embodiments)
20, 20A ... Plunger part 21, 21A ... Plunger 211, 211a ... Large diameter part 212a ... Medium diameter part 213, 213a ... Small diameter part 214 ... Stepped part 214a ... First stepped portion (fifth embodiment)
214b ... Second stepped portion (fifth embodiment)
23, 23A ... Plunger stopper (first embodiment)
231 ... Bottom part 232, 232a ... Stopper part 233 ... Outer wall part 234 ... Bent part 24 ... Fuel seal member 25, 25A ... Seal elements 34, 34A to 34E, 37 ... -Plunger stopper (third and fourth embodiments)
35, 35A to 35E ... 1st ring 351, 351a to 351e, 371 ... Engagement part 36, 36D, 36E ... 2nd ring 363, 363e, 373, 373a ... Projection part 366, 376 ... Communication path 367 ... Notch 368, 377, 378 ... Stopper 38 ... Plunger stopper (fifth embodiment)
382... Stopper 90... Cylinder forming member (sixth embodiment)

Claims (11)

A cylinder forming member (10, 90) having a cylinder hole (11, 91) and a pressurizing chamber (12, 92) communicating with the cylinder hole;
A plunger (21) having a sliding surface that slides along the inner wall surface of the cylinder hole, and sucking and pressurizing fuel into the pressurizing chamber by reciprocating in the cylinder hole in the axial direction;
The cylinder forming member is detachably attached to a cylindrical cylinder hole forming portion (14) including a cylinder end portion (141) opposite to the pressurizing chamber and protruding to the opposite side of the pressurizing chamber, and the plunger A plunger stopper (34, 37) that cooperates with a stepped portion formed at a predetermined position to restrict the movement of the plunger in a state where the sliding surface of the plunger is in contact with the inner wall surface of the cylinder hole. When,
With
The plunger has a large-diameter portion (211) having an end portion facing the pressurizing chamber and having the sliding surface, and extends from the large-diameter portion to the opposite side of the pressurizing chamber and has an outer diameter larger than that of the large-diameter portion. And a first stepped portion (214) that forms a boundary between the large diameter portion and the small diameter portion, and the first stepped portion cooperates with the plunger stopper. The stepped portion to be
The plunger stopper includes a stopper portion (368, 377, 378) with which the stepped portion comes into contact with the movement of the plunger in the cylinder hole, and an outer wall surface of the cylinder hole forming portion of the cylinder forming member. A high pressure pump (1, 3, 6) comprising a plurality of engaging portions (351, 371) engaged with (142).   2. The high-pressure pump according to claim 1, wherein the engaging portion is pressed against an outer wall surface of the cylinder hole forming portion of the cylinder forming member by an elastic force in a radially inward direction.   3. The high-pressure pump according to claim 1, further comprising a convex portion (363, 373) that abuts on the cylinder end portion of the cylinder forming member between a plurality of the engaging portions in the circumferential direction. 3).   4. The high pressure according to claim 3, wherein communication paths (366, 376) that connect the inner radial direction and the outer radial direction of the plunger stopper are formed between the circumferential directions of the plurality of convex portions. pump.   5. The high-pressure pump according to claim 3, wherein the stopper portion is formed on a radially inner side of inner walls of the plurality of convex portions.   The plunger stopper (34) includes a first ring (35) having the engaging portion, and a second ring (36) having the convex portion and provided separately from the first ring. The high pressure pump according to any one of claims 3 to 5, wherein The engaging portion (351) of the first ring is formed to extend from the outer edge of the annular main body toward the pressurizing chamber in the axial direction.
The second ring has a notch (367) that can be engaged with at least a part of the engaging portion at a position corresponding to the engaging portion in the circumferential direction, and the engaging portion is notched. The high pressure pump according to claim 6, wherein the high pressure pump is combined with the first ring while engaging with a portion. Outer recesses (15, 93) are formed on the outer wall surface of the cylinder hole forming portion of the cylinder forming member,
The high-pressure pump according to any one of claims 1 to 7, wherein the plunger stopper is fixedly attached to the outer recess. The high-pressure pump according to any one of claims 1 to 8,
The high-pressure pump characterized in that the cylinder forming member (10) is continuously integrated with a pump body that forms an outline of the high-pressure pump. A cylinder forming member (10) having a cylinder hole (11) and a pressurizing chamber (12) communicating with the cylinder hole;
A plunger (21A) that has a sliding surface that slides along the inner wall surface of the cylinder hole, and draws and pressurizes fuel into the pressurizing chamber by reciprocating in the cylinder hole in the axial direction;
The cylinder forming member is attached to a cylindrical cylinder hole forming portion (14) including a cylinder end portion (141) opposite to the pressurizing chamber and protruding to the opposite side of the pressurizing chamber. A plunger stopper (38) that cooperates with a stepped portion formed at a position and regulates the movement of the plunger in a state where the sliding surface of the plunger is in contact with the inner wall surface of the cylinder hole;
With
The plunger has a large-diameter portion (211a) whose end faces the pressurizing chamber and has the sliding surface, and extends from the large-diameter portion to the opposite side of the pressurizing chamber and has an outer diameter larger than the large-diameter portion. Medium diameter part (212a) having a small diameter, a small diameter part (213a) extending from the medium diameter part to the opposite side of the pressurizing chamber and having an outer diameter smaller than the medium diameter part, the medium diameter part and the small diameter part A second stepped portion (214b) that forms a boundary with the second stepped portion, the stepped portion cooperating with the plunger stopper,
The plunger stopper has a stopper portion (382) with which the stepped portion comes into contact with the movement of the plunger in the cylinder hole, and the distance between the stopper portion and the cylinder end portion of the cylinder forming member (L1) is the same as the length (L2) in the axial direction of the cylinder hole of the medium diameter portion or shorter than the length of the medium diameter portion in the axial direction of the cylinder hole ( 5).   A fuel seal member (24) that slidably contacts the outer wall surface of the medium diameter portion and suppresses fuel leakage accompanying reciprocal movement of the plunger is provided between the cylinder end portion of the cylinder forming member and the plunger stopper. The high-pressure pump according to claim 10, wherein the high-pressure pump is disposed between the stopper portion.

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