JP5321982B2 - High pressure pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a high pressure pump which suppresses operational malfunction and can highly accurately control a discharge amount. <P>SOLUTION: A housing body 11 includes: a pressurizing chamber 113 in which fuel is pressurized; a cylindrical passage wall face 152 forming a passage 151 leading the fuel into the pressurizing chamber 113; a locking groove 153 recessed in a radially outside direction of the passage wall face 152; and an annular wall face 154 extended between the locking groove 153 and the pressurizing chamber 113 in a radial direction of a passage wall face 152 and formed to be approximately annular. A valve body 30 has a valve seat 34 disposed to a wall face on a pressurizing chamber 113 side. The valve member 40 seats on or is separated from the valve seat 34 to cut off or flow the fuel flowing through the passage 151. A locking member 60 is fitted in the locking groove 153 and abuts on the valve body 30 to lock the valve body 30. A leaf spring 80 is formed to be approximately annular, is disposed between the valve body 30 and the annular wall face 154, and is elastically deformed in an axial direction to press the valve body 30 against the locking member 60. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a high-pressure pump that pressurizes fuel sucked into a pressurizing chamber.

  Conventionally, a high pressure pump that pressurizes and discharges fuel sucked into a pressurizing chamber by a reciprocating movement of a plunger is known. For example, in the high-pressure pump disclosed in Patent Document 1, the valve body and the valve seat of the valve body are seated on or separated from the valve seat in the middle of the fuel passage connected to the pressurization chamber. And a valve member for adjusting the flow rate of the supplied fuel. The housing of the high-pressure pump includes a cylindrical passage wall surface that forms the fuel passage, a locking groove that is formed so as to be recessed in a radially outward direction of the passage wall surface, and the locking groove and the pressurizing chamber. A wall surface (hereinafter referred to as “annular wall surface”) that extends in the radial direction of the passage wall surface and is formed in an annular shape. A C-ring-shaped or split-plate-shaped locking member is fitted in the locking groove. The valve body is provided between the locking member and the annular wall surface. In this high-pressure pump, the valve body is locked by the locking member, and the valve body is prevented from coming out to the side opposite to the pressurizing chamber.

  By the way, the pressure chamber side of the valve body becomes high pressure when the fuel is pressurized in the pressure chamber, and becomes low pressure when the fuel is sucked into the pressure chamber. In this high-pressure pump, a gap is formed between the valve body and the annular wall surface (see FIG. 1). The position fluctuates between. As a result, the initial position of the needle that contacts the opposite side of the valve member from the pressurizing chamber also varies. For this reason, the responsiveness of the valve member may fluctuate and it may be difficult to control the discharge amount. Moreover, when the electromagnetic drive part which attracts | sucks a needle and the needle will be in the state which left | separated more than predetermined distance, a needle cannot be attracted | sucked by an electromagnetic drive part, and there exists a possibility that the malfunction of a valve member may arise.

  On the other hand, Patent Document 2 discloses a high-pressure pump in which an annular pressure pulsation transmission blocking member is provided between a valve body and an annular wall surface (see FIG. 4).

European Patent Application No. 1413756 Japanese Patent No. 3851056

  Patent Document 2 describes that “the height of the pressure pulsation transmission blocking member is made equal to or less than the distance between the valve body and the annular wall surface”. Therefore, even if the configuration (pressure pulsation transmission preventing member) described in Patent Document 2 is applied to the high-pressure pump of Patent Document 1, the position of the valve body varies between the locking member and the annular wall surface. obtain. Therefore, even if the configuration of the high-pressure pump disclosed in Patent Document 1 and the configuration of the high-pressure pump disclosed in Patent Document 2 are combined, the problem caused by the high-pressure pump disclosed in Patent Document 1 cannot be solved. When “the height of the pressure pulsation transmission blocking member is the same as the distance between the valve body and the annular wall surface”, a gap between the valve body and the annular wall surface can be filled. However, a clearance for inserting the locking member into the locking groove is formed between the wall surface of the locking groove and the locking member, and play occurs between the locking groove and the locking member. it is conceivable that. Therefore, even with such a configuration (a configuration in which the height of the pressure pulsation transmission preventing member is the same as the distance between the valve body and the annular wall surface), the above problem cannot be solved. Further, in such a configuration, the pressure pulsation transmission blocking member has a pressure inside the pressure chamber equal to that of the pressure chamber, so that a differential pressure is repeatedly generated between the inside and outside of the pressure pulsation transmission blocking member during pump operation. As a result, the pressure pulsation transmission preventing member may be damaged.

The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a high-pressure pump capable of suppressing malfunction and controlling the discharge amount with high accuracy.
Another object of the present invention is to provide a high-pressure pump that is capable of suppressing malfunction and controlling the discharge amount with high accuracy and having high durability.

  The invention according to claim 1 is a high pressure pump comprising a plunger, a housing, a valve body, a valve member, a first urging member, a needle, a second urging member, an electromagnetic drive unit, a locking member, and an elastic member. It is an invention. The housing includes a pressurizing chamber in which fuel is pressurized by a plunger, a substantially cylindrical passage wall surface that forms a fuel passage that guides fuel to the pressurizing chamber, a locking groove that is recessed radially outward of the passage wall surface, and It has an annular wall surface that extends in the radially inward direction of the passage wall surface between the locking groove and the pressurizing chamber and is formed in a substantially annular shape. The valve body is provided on the side opposite to the pressurizing chamber on the annular wall surface, and has a valve seat on the wall surface on the pressurizing chamber side. The valve member intermittently flows the fuel flowing through the fuel passage by being seated on the valve seat or separated from the valve seat.

  The first urging member is provided on the pressure chamber side of the valve member and urges the valve member in the valve closing direction. The needle is provided so as to be able to contact or connect to the end of the valve member opposite to the pressurizing chamber, and can be moved in the same direction as the valve member when the valve member is opened or closed. is there. The second urging member urges the needle in the valve opening direction of the valve member. The electromagnetic drive unit has a coil unit that can attract the needle in either the valve closing direction or the valve opening direction of the valve member.

  The locking member is fitted in a locking groove formed in the housing, and can lock the valve body by coming into contact with a wall surface of the valve body opposite to the pressurizing chamber. Thereby, it can suppress that a valve body slips out to the opposite side to a pressurization chamber. The elastic member is formed in a substantially annular shape, and is provided between the valve body and the annular wall surface. The elastic member presses the valve body against the locking member by elastically deforming in the axial direction. Thereby, the position of the valve body is stabilized in a state where the valve body is in contact with the locking member. Therefore, even if the pressure in the pressurizing chamber varies during the operation of the high-pressure pump, the valve body can keep its position without being affected by the pressure variation in the pressurizing chamber. With this configuration, even if the pressure in the pressurizing chamber fluctuates, fluctuations in the initial position of the needle are suppressed. Therefore, fluctuations in the responsiveness of the valve member are suppressed, and the amount of fuel discharged from the high-pressure pump can be controlled with high accuracy. In addition, according to the present invention, it is possible to suppress the electromagnetic drive unit that attracts the needle from being separated from the needle by a predetermined distance or more, and thus it is possible to suppress malfunction of the valve member.

  Further, in the present invention, since the elastic member presses the valve body against the locking member, the locking member is pressed against the wall surface of the locking groove. Therefore, it is possible to suppress the occurrence of backlash between the locking groove and the locking member.

According to the first aspect of the present invention, at least one of the elastic member side end surface, the annular wall surface, and the elastic member of the valve body is formed with a communication path that connects the inside and the outside of the elastic member. . Thereby, since the fuel can flow between the inside and the outside of the elastic member through the communication path, the pressure inside the elastic member and the pressure outside can be made the same. Therefore, even if the pressure inside the elastic member fluctuates because the pressure in the pressurizing chamber fluctuates during the operation of the high-pressure pump, it is possible to suppress the occurrence of a differential pressure between the inside and outside of the elastic member. . Therefore, damage to the elastic member can be suppressed. Therefore, an elastic member can be used over a long period of time, and durability of a high pressure pump can be improved.

Elastic members provided in the invention described in claim 1, as a more specific configuration, it is conceivable also to the following.

In the invention described in claim 1, the elastic member is Ri Ah in disc spring, a tapered tubular portion having a tapered inner and outer walls, annularly radially inwardly from one axial end portion of the tapered tubular portion An inner flange portion that extends, and an outer flange portion that extends in an annular shape radially outward from the other axial end portion of the tapered tube portion. The boundary portion between the outer flange and the tapered tube portion, and the boundary portion between the inner flange portion and the tapered tube portion, that is formed into a curved shape. When a general disc spring is installed between the valve body and the annular wall surface, the disc spring is in a state where both ends in the axial direction are in contact with the valve body and the annular wall surface without gaps, so the fuel is inside the disc spring. And the outside cannot be circulated. In this case, a differential pressure is generated between the inside and the outside of the disc spring, and the disc spring may be damaged. In the present invention, at least one of the elastic member (disc spring) side end surface, the annular wall surface, and the elastic member (disc spring) of the valve body communicates with the inside and the outside of the elastic member (disc spring). Is formed. Therefore, even if the elastic member is a disc spring, the fuel can flow between the inside and the outside of the elastic member through the communication path, so the pressure inside and outside the elastic member (disc spring) is the same. can do. Thereby, the breakage of the disc spring can be suppressed. In addition, as a specific method of providing the communication path in the disc spring, for example, there is a proposal that a hole that communicates the inside and the outside is formed in the tapered cylindrical portion constituting the disc spring and this is used as the communication path. It is done.

  In the invention according to claim 4, the elastic member is a wave spring. It can be said that the wave spring has a communication path (gap) that communicates the inside and the outside of the wave spring in a state where both end portions in the axial direction are in contact with the valve body and the annular wall surface. For this reason, when a wave spring is used as the elastic member, it is not necessary to separately provide a communication path in at least one of the elastic member (wave spring) side end surface, the annular wall surface, and the elastic member (wave spring) of the valve body. . Therefore, the manufacturing cost can be reduced while improving the durability of the high-pressure pump. Even when a wave spring is used as the elastic member, a separate communication path may be provided on at least one of the end face and the annular wall surface of the valve body on the elastic member (wave spring) side.

The fragmentary sectional view of the high-pressure pump by a 1st embodiment of the present invention. 1 is a cross-sectional view of a high pressure pump according to a first embodiment of the present invention. It is a figure which shows the elastic member of the high pressure pump by 1st Embodiment of this invention, Comprising: (A) is a top view, (B) is a BB sectional drawing of (A), (C) is (B). The enlarged view of the C section shown. (A) is sectional drawing which shows a part of elastic member of the high-pressure pump by 1st Embodiment of this invention, and its vicinity, (B) is BB sectional drawing of (A). It is typical sectional drawing for demonstrating the difference between the elastic member of the high-pressure pump by 1st Embodiment of this invention, and the elastic member of a comparative example, Comprising: (A) is sectional drawing of the elastic member of a comparative example, (B ) Is an enlarged view of a portion B shown in (A), (C) is a sectional view of the elastic member of the present invention, and (D) is an enlarged view of a portion D shown in (C). It is a figure for demonstrating the difference between the elastic member of the high-pressure pump by 1st Embodiment of this invention, and the elastic member of a comparative example, Comprising: (A) is the "surface which the axial direction edge part of the elastic member of a comparative example receives" FIG. 5B is a diagram showing a relationship between “pressure” and “contact width”, and FIG. 5B is a relationship between “contact width” and “deformation amount” when the elastic member of the present invention and the elastic member of the comparative example are subjected to surface pressure. FIG. It is a figure which shows the valve body of the high pressure pump by 2nd Embodiment of this invention, Comprising: (A) is a top view, (B) is the BB sectional drawing of (A). It is a figure which shows the valve body of the high pressure pump by 3rd Embodiment of this invention, Comprising: (A) is a top view, (B) is the BB sectional drawing of (A). The top view which shows the valve body of the high pressure pump by 4th Embodiment of this invention. The top view which shows the valve body of the high pressure pump by 5th Embodiment of this invention. Sectional drawing which shows a part of elastic member of the high-pressure pump by 6th Embodiment of this invention, and its vicinity. Sectional drawing which shows a part of elastic member of the high-pressure pump by 7th Embodiment of this invention, and its vicinity. Sectional drawing which shows a part of elastic member of the high-pressure pump by 8th Embodiment of this invention, and its vicinity.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. Note that, in a plurality of embodiments, substantially the same components are denoted by the same reference numerals, and description thereof is omitted.
(First embodiment)
A high-pressure pump according to an embodiment of the present invention and a part thereof are shown in FIGS. The high-pressure pump 10 is a fuel pump that supplies fuel to, for example, an injector of a diesel engine or a gasoline engine.

As shown in FIG. 2, the high-pressure pump 10 includes a housing body 11, a cover 12, a plunger 13, a valve body 30, a valve member 40, a spring 21, a needle 49, a spring 22, an electromagnetic driving unit 70, a locking member 60, and A disc spring 80 is provided.
The housing main body 11 and the cover 12 constitute a “housing” in the claims. The housing body 11 is made of, for example, martensitic stainless steel. The housing body 11 forms a cylindrical cylinder 14. A plunger 13 is supported on the cylinder 14 of the housing body 11 so as to be reciprocally movable in the axial direction.

  The housing body 11 forms an introduction passage 111, a suction passage 112, a pressurizing chamber 113, a discharge passage 114, and the like. The housing body 11 has a cylindrical portion 15. The cylinder portion 15 forms a passage 151 that communicates the introduction passage 111 and the suction passage 112 therein. Here, the passage 151 constitutes a part of the “fuel passage” in the claims. The passage 151 is formed by being surrounded by a cylindrical passage wall surface 152 which is an inner wall of the cylindrical portion 15. In the present embodiment, the cylindrical portion 15 has a locking groove 153 that is recessed in the radially outward direction of the passage wall surface 152 and is formed in an annular shape along the passage wall surface 152. An inner diameter of the end portion of the passage 151 on the pressurizing chamber 113 side is small. As a result, an annular wall surface 154 is formed between the locking groove 153 of the passage 151 and the pressurizing chamber 113 and extends annularly in the radially inward direction of the passage wall surface 152. The valve body 30 is provided inside the passage wall surface 152 and between the locking groove 153 and the annular wall surface 154. That is, the valve body 30 is provided on the opposite side of the annular wall surface 154 from the pressurizing chamber 113.

  A fuel chamber 16 is formed between the housing body 11 and the cover 12. A fuel inlet (not shown) that communicates with the fuel chamber 16 is formed in the housing body 11. Fuel is supplied to the fuel chamber 16 from a fuel tank by a low-pressure fuel pump (not shown) through the fuel inlet. The introduction passage 111 communicates the fuel chamber 16 and a passage 151 formed on the inner peripheral side of the cylindrical portion 15. One end of the suction passage 112 communicates with the pressurizing chamber 113. The other end of the suction passage 112 opens to the inner peripheral side of the annular wall surface 154. The introduction passage 111 and the suction passage 112 are connected via the inner peripheral side of the valve body 30 as shown in FIG. As shown in FIG. 2, the pressurizing chamber 113 communicates with the discharge passage 114 on the side opposite to the suction passage 112. Here, the introduction passage 111, the passage 151, and the suction passage 112 constitute a “fuel passage” in the claims. In the present embodiment, the “fuel passage” is indicated by the fuel passage 100.

  The plunger 13 is supported on the cylinder 14 of the housing body 11 so as to be reciprocally movable in the axial direction. The pressurizing chamber 113 is formed on one end side in the reciprocating direction of the plunger 13. A head 17 provided on the other end side of the plunger 13 is coupled to a spring seat 18. A spring 19 is provided between the spring seat 18 and the oil seal holder 28 fixed to the housing body 11. The spring seat 18 is biased toward the cam (not shown) by the biasing force of the spring 19. The plunger 13 is driven to reciprocate by contacting a cam via a tappet (not shown).

  The spring 19 has one end in contact with the oil seal holder 28 and the other end in contact with the spring seat 18. The spring 19 has a force that extends in the axial direction. As a result, the spring 19 biases a tappet (not shown) to the cam side via the spring seat 18. A space between the outer peripheral surface of the plunger 13 on the head 17 side and the oil seal holder 28 is liquid-tightly sealed with an oil seal 23. The oil seal 23 prevents oil from entering the pressurizing chamber 113 from the engine and prevents fuel from flowing out from the pressurizing chamber 113 to the engine.

  The discharge valve portion 90 that forms the fuel outlet 91 is provided on the discharge passage 114 side of the housing body 11. The discharge valve unit 90 intermittently discharges the fuel pressurized in the pressurizing chamber 113. The discharge valve unit 90 includes a check valve 92, a regulating member 93, and a spring 94. The check valve 92 is formed in a bottomed cylindrical shape including a bottom portion 921 and a cylindrical portion 922 that extends in a cylindrical shape from the bottom portion 921 toward the anti-pressurization chamber 113, and is provided so as to be capable of reciprocating in the discharge passage 114. The regulating member 93 is formed in a cylindrical shape and is fixed to the housing body 11 that forms the discharge passage 114. One end of the spring 94 is in contact with the regulating member 93, and the other end is in contact with the cylindrical portion 922 of the check valve 92. The check valve 92 is biased toward the valve seat 95 formed by the housing body 11 by the biasing force of the spring 94. The check valve 92 closes the discharge passage 114 when the end portion on the bottom 921 side is seated on the valve seat 95, and opens the discharge passage 114 when the end portion is separated from the valve seat 95. When the check valve 92 moves to the side opposite to the valve seat 95, the movement of the check valve 92 is restricted by the end of the cylinder portion 922 on the side opposite to the bottom 921 contacting the restriction member 93.

  When the pressure of the fuel in the pressurizing chamber 113 increases, the force received by the check valve 92 from the fuel on the pressurizing chamber 113 side increases. The force received by the check valve 92 from the fuel on the pressurizing chamber 113 side is larger than the sum of the biasing force of the spring 94 and the fuel received from the fuel on the downstream side of the valve seat 95, that is, the fuel in the delivery pipe (not shown). As a result, the check valve 92 is separated from the valve seat 95. As a result, the fuel in the pressurizing chamber 113 is discharged from the fuel outlet 91 via the discharge passage 114, that is, the through hole 923 formed in the cylindrical portion 922 of the check valve 92 and the inner side of the cylindrical portion 922. Is discharged to the outside.

  On the other hand, when the pressure of the fuel in the pressurizing chamber 113 decreases, the force that the check valve 92 receives from the fuel on the pressurizing chamber 113 side decreases. When the force received by the check valve 92 from the fuel on the pressurizing chamber 113 side becomes smaller than the sum of the urging force of the spring 94 and the force received from the fuel on the downstream side of the valve seat 95, the check valve 92 is Sitting on 95. As a result, fuel in a delivery pipe (not shown) is prevented from flowing into the pressurizing chamber 113 via the discharge passage 114.

  As shown in FIG. 1, the valve body 30 is provided inside the passage wall surface 152 and between the locking groove 153 and the annular wall surface 154. The valve body 30 is locked inside the passage wall surface 152 by a locking member 60 fitted in the locking groove 153 and a disc spring 80 as an elastic member provided on the annular wall surface 154. The locking member 60 and the disc spring 80 will be described in detail later.

  The valve body 30 is formed in a bottomed cylindrical shape including a bottom portion 31 and a cylindrical portion 32 that extends from the bottom portion 31 toward the pressurizing chamber 113. The valve body 30 has a recess 33 that is recessed toward the anti-pressurization chamber 113 on the pressurization chamber 113 side of the bottom 31. A valve seat 34 is formed on the outer edge of the recess 33 on the wall surface of the bottom 31 on the pressurizing chamber 113 side. That is, the valve body 30 has a valve seat 34 on the side wall surface of the pressurizing chamber 113. The valve seat 34 is formed in a tapered shape that forms a predetermined angle with respect to the axis of the valve body 30.

  The valve body 30 has a first guide portion 35 at the center of the bottom portion 31. The 1st guide part 35 is formed so that it may protrude in the cylinder shape from the center part of the bottom part 31 to the anti-recession 33 side. The valve body 30 has a first insertion hole 351 that connects the wall surface forming the recess 33 of the first guide portion 35 and the wall surface on the opposite recess 33 side. Further, on the outer peripheral side of the first insertion hole 351 in the bottom portion 31, a first passage 121 that connects the wall surface that forms the recess 33 and the wall surface on the opposite recess 33 side is formed. A plurality of first passages 121 are formed in the circumferential direction with respect to the axis of the valve body 30.

  An annular seal member 36 and a backup ring 37 are provided between the outer peripheral wall of the cylindrical portion 32 of the valve body 30 and the passage wall surface 152. The seal member 36 and the backup ring 37 are provided in an annular groove formed on the outer periphery of the cylindrical portion 32. The seal member 36 is in close contact with the cylindrical portion 32 and the passage wall surface 152, thereby preventing fuel from leaking between the pressurizing chamber 113 and the introduction passage 111 through the space between the outer peripheral wall of the cylindrical portion 32 and the passage wall surface 152. ing.

  The valve member 40 includes a substantially cylindrical shaft portion 41 and a substantially disk-shaped umbrella portion 42 connected to the end portion of the shaft portion 41 on the pressurizing chamber 113 side. The valve member 40 is provided such that the shaft portion 41 is inserted into the first insertion hole 351 of the first guide portion 35 and can reciprocate in the axial direction of the shaft portion 41 inside the valve body 30. The wall surface on the valve seat 34 side of the umbrella portion 42 corresponds to the shape of the valve seat 34 and is formed in a tapered shape that forms a predetermined angle with respect to the shaft of the shaft portion 41. The valve member 40 reciprocates, so that the umbrella portion 42 is seated on the valve seat 34 or is separated from the valve seat 34 to interrupt the flow of fuel flowing through the fuel passage 100. Further, the valve member 40 forms an annular second passage 122 between the valve member 40 and the valve seat 34 when the umbrella portion 42 is separated from the valve seat 34.

  The diameter of the first insertion hole 351 of the first guide part 35 is substantially the same as the diameter of the shaft part 41 of the valve member 40 or slightly larger than the diameter of the shaft part 41. Thus, the valve member 40 reciprocates inside the valve body 30 while the outer wall of the shaft portion 41 slides on the wall surface of the first guide portion 35 that forms the first insertion hole 351. Therefore, when the valve member 40 reciprocates, the reciprocating movement is guided by the first guide portion 35.

  A stopper 50 is provided on the pressure chamber 113 side of the valve member 40. The stopper 50 includes a cylindrical portion 51, a bottom portion 52 that closes an end portion of the cylindrical portion 51 on the counter valve member 40 side, and an annular extended portion 53 that is formed on a radially outer side of the bottom portion 52. The stopper 50 is fixed to the valve body 30 by welding the outer peripheral wall of the extended portion 53 to the inner peripheral wall of the cylindrical portion 32 of the valve body 30.

  A spring 21 as a first biasing member is provided between the stopper 50 and the valve member 40. One end of the spring 21 is in contact with the bottom 52 and the other end is in contact with the valve member 40 inside the cylindrical portion 51 of the stopper 50. The spring 21 has a force extending in the axial direction, and biases the valve member 40 toward the counter stopper 50 side, that is, in the valve closing direction.

The end portion on the valve member 40 side of the tubular portion 51 of the stopper 50 and the end portion on the stopper 50 side of the valve member 40 can contact each other. The stopper 50 forms a volume chamber 54 surrounded by the valve member 40, the inner wall of the cylindrical portion 51, and the bottom portion 52 when the valve member 40 contacts the stopper 50. At this time, the stopper 50 restricts the movement of the valve member 40 toward the pressurizing chamber 113, that is, in the valve opening direction.
When the valve member 40 is in contact with the cylindrical portion 51 of the stopper 50, the stopper 50 covers the pressurizing chamber 113 side of the valve member 40. Thereby, at this time, the fuel traveling from the pressurizing chamber 113 side to the valve member 40 side is alleviated from colliding with the valve member 40.

A third passage 123 that connects the wall surface on the pressurizing chamber 113 side and the wall surface on the anti-pressurizing chamber 113 side of the expanding portion 53 is formed in the expanding portion 53 of the stopper 50. A plurality of third passages 123 are formed in the circumferential direction with respect to the axis of the stopper 50.
Between the second passage 122 and the third passage 123, a substantially annular intermediate passage 124 surrounded by the inner peripheral wall of the cylindrical portion 32 of the valve body 30 and the outer peripheral wall of the cylindrical portion 51 of the stopper 50 is formed. Yes. A communication passage 55 that connects the volume chamber 54 and the intermediate passage 124 is formed in the cylindrical portion 51 of the stopper 50.

  The first passage 121, the second passage 122, the third passage 123, and the intermediate passage 124 described above are included in the passage 151 formed in the housing body 11, respectively. That is, the fuel passage 100 includes a first passage 121, a second passage 122, a third passage 123, and an intermediate passage 124. Thus, when the fuel moves from the fuel chamber 16 side to the pressurizing chamber 113 side, the fuel flows through the first passage 121, the second passage 122, the intermediate passage 124, and the third passage 123 in this order. On the other hand, when the fuel goes from the pressurizing chamber 113 side to the fuel chamber 16 side, the fuel flows through the third passage 123, the intermediate passage 124, the second passage 122, and the first passage 121 in this order.

  As shown in FIG. 2, the electromagnetic drive unit 70 includes a coil 71, a fixed core 72, a movable core 73, a flange 75, and the like. The coil 71 is wound around a spool 78 made of resin, and generates a magnetic field when energized. The fixed core 72 is made of a magnetic material. The fixed core 72 is accommodated on the inner peripheral side of the coil 71. The movable core 73 is made of a magnetic material. The movable core 73 is disposed to face the fixed core 72. The movable core 73 is accommodated on the inner peripheral side of the cylindrical member 79 and the flange 75 made of a nonmagnetic material so as to be capable of reciprocating in the axial direction. The cylindrical member 79 prevents a magnetic short circuit between the fixed core 72 and the flange 75.

  The flange 75 is made of a magnetic material. As shown in FIG. 1, the flange 75 is attached to the cylindrical portion 15 of the housing body 11. As a result, the flange 75 holds the electromagnetic drive unit 70 on the housing body 11 and closes the end portion of the cylindrical portion 15. The flange 75 has the 2nd guide part 76 formed in the cylinder shape in the center part. The second guide portion 76 has a second insertion hole 761 that communicates the valve body 30 side and the counter valve body 30 side of the flange 75.

  The needle 49 is formed in a substantially cylindrical shape, and is inserted into a second insertion hole 761 formed in the second guide portion 76 of the flange 75. The needle 49 is provided so as to be capable of reciprocating in the axial direction inside the second insertion hole 761. The diameter of the second insertion hole 761 is substantially the same as the diameter of the needle 49 or slightly larger than the diameter of the needle 49. Thereby, the needle 49 reciprocates while the outer wall slides on the wall surface of the second guide portion 76 forming the second insertion hole 761. Therefore, when the needle 49 reciprocates, the reciprocating movement is guided by the second guide portion 76.

  One end of the needle 49 is press-fitted or welded to the movable core 73 so as to be integrated with the movable core 73. Further, the other end of the needle 49 can come into contact with the end of the shaft portion 41 of the valve member 40 on the side opposite to the umbrella portion 42. The needle 49 is movable in the same direction as the movement direction when the valve member 40 is opened or closed.

  A spring 22 as a second biasing member is provided between the fixed core 72 and the movable core 73. The spring 22 biases the movable core 73 toward the valve member 40 side. The force with which the spring 22 biases the movable core 73 is larger than the force with which the spring 21 biases the valve member 40. That is, the spring 22 urges the movable core 73 and the needle 49 against the urging force of the spring 21 in the valve member 40 side, that is, in the valve opening direction of the valve member 40. Thereby, when the coil 71 is not energized, the fixed core 72 and the movable core 73 are separated from each other. Therefore, when the coil 71 is not energized, the needle 49 integral with the movable core 73 moves to the valve member 40 side by the biasing force of the spring 22, and the valve member 40 moves away from the valve seat 34 of the valve body 30. ing. The coil 71, the fixed core 72, the movable core 73, the flange 75, the spool 78, and the cylindrical member 79 of the electromagnetic drive unit 70 constitute a “coil unit” in the claims.

Next, the locking member 60, the disc spring 80, and the vicinity thereof will be described.
As shown in FIG. 1, in this embodiment, the locking member 60 is composed of two plate members (a plate member 61 and a plate member 62). The plate member 61 and the plate member 62 are formed of a metal such as stainless steel, for example, and are subjected to heat treatment so as to have a predetermined hardness. The plate member 61 is formed in an arc shape. The plate member 62 is also formed in an arc shape like the plate member 61. The plate member 61 and the plate member 62 are fitted into an annular locking groove 153 formed in the housing body 11 and abut on the wall surface of the valve body 30 opposite to the pressurizing chamber 113, thereby The body 30 can be locked.

  The plate member 61 and the plate member 62 have an annular shape in a state where the respective end portions are in contact with each other. In this state, the locking member 60 has an annular step surface formed at its inner peripheral end so as to be recessed to a position that is a predetermined distance away from the surface on the valve body 30 side in the axial direction. A C-ring 600 is provided between the step surface and the valve body 30, that is, inside the locking member 60.

  The C ring 600 is formed in a substantially C shape by using a metal such as stainless steel. In a state where the C ring 600 is provided inside the locking member 60, the C ring 600 has an elastic force in the radially outward direction. Accordingly, the C ring 600 suppresses the locking member 60 from dropping from the locking groove 153 by pressing the locking member 60 (the plate member 61 and the plate member 62) in the radially outward direction.

  The disc spring 80 is formed in a substantially annular shape, as shown in FIG. The disc spring 80 is formed by pressing a thin plate made of a metal such as stainless steel. The disc spring 80 is designed to have a predetermined strength and fatigue durability, and may be subjected to heat treatment. As shown in FIG. 3 (B), the disc spring 80 has a tapered cylindrical portion 81 having a tapered inner wall and an outer wall, and extends in an annular shape radially inward from one axial end portion of the tapered cylindrical portion 81. An inner flange portion 82 and an outer flange portion 83 extending in an annular shape radially outward from the other axial end portion of the tapered tube portion 81. With this configuration, the disc spring 80 has a force (elastic force) that extends in the axial direction when pressed in a direction in which both ends in the axial direction contract. In this embodiment, since the disc spring 80 is formed by pressing, as shown in FIG. 3C, the boundary portion between the outer flange portion 83 and the tapered cylindrical portion 81, and the inner flange portion. A boundary portion between 82 and the tapered cylindrical portion 81 is formed in a relatively smooth curved surface.

  As shown in FIGS. 1 and 4A, the disc spring 80 is provided between the annular annular wall surface 154 formed in the housing body 11 and the valve body 30. The height of the disc spring 80, that is, the length in the axial direction is set to be larger than the distance between the valve body 30 and the annular wall surface 154 when the valve body 30 is in contact with the locking member 60. Therefore, when the disc spring 80 is provided between the valve body 30 and the annular wall surface 154, an elastic force is generated in the axial direction and presses the valve body 30 against the locking member 60.

  With this configuration, the valve body 30 is pressed to the opposite side of the pressurizing chamber 113 by the disc spring 80 and is locked to the locking member 60 by contacting the locking member 60. Therefore, the position of the valve body 30 is stabilized inside the passage wall surface 152. Here, the elastic force generated by the disc spring 80 may be set to a magnitude that does not cause the valve body 30 to move in the axial direction even if the pressure in the pressurizing chamber 113 fluctuates when the high-pressure pump 10 is operated. desirable. Further, by locking the valve body 30 with the locking member 60, it is possible to suppress the valve body 30 from coming out to the side opposite to the pressurizing chamber 113.

As shown in FIGS. 4A and 4B, the end surface 38 of the cylindrical portion 32 of the valve body 30 on the side of the disc spring 80 is provided with a communication passage 301 formed so as to be recessed toward the opposite side of the disc spring 80. It has been. The communication path 301 is formed so as to extend in the radially outward direction of the annular end surface 38. In the present embodiment, the communication passage 301 is formed at two positions in the circumferential direction of the end face 38 and at positions substantially opposite to each other across the center of the end face 38 (see FIG. 1).
The communication path 301 can communicate the inside and the outside of the disc spring 80 in a state where the disc spring 80 is in contact with the valve body 30 and the annular wall surface 154. That is, a communication passage 301 that connects the inside and the outside of the disc spring 80 is formed on the end surface 38 of the valve body 30 on the disc spring 80 side.

  In the above configuration, when the fuel flows through the communication path 301, the pressures on the inner side and the outer side of the disc spring 80 become substantially the same. The inside of the disc spring 80 and the pressurizing chamber 113 are always in communication. Therefore, when the pressure in the pressurizing chamber 113 fluctuates, the pressure inside the disc spring 80 also fluctuates, but the occurrence of a differential pressure between the inside and the outside of the disc spring 80 is suppressed.

Next, assembly of the valve body 30, the locking member 60, the C ring 600, and the disc spring 80 to the housing body 11 will be described with reference to FIG.
(1) The disc spring 80 is installed so as to contact the annular wall surface 154 of the housing body 11.
(2) A passage in which the valve body 30, the valve member 40, the stopper 50, the spring 21, the seal member 36, and the backup ring 37 are integrated so that the pressurizing chamber 113 side end of the valve body 30 contacts the disc spring 80. Insert inside the wall surface 152.
(3) Inside the passage wall surface 152 so that the locking member 60 in a state where the ends of the plate member 61 and the plate member 62 are in contact with each other is in contact with the end of the valve body 30 opposite to the pressurizing chamber 113. Insert into.
(4) The locking member 60 is slid so as to spread outward in the radial direction while being pressed toward the pressurizing chamber 113 against the elastic force of the disc spring 80 and is fitted into the locking groove 153.
(5) The C ring 600 is installed inside the locking member 60.

  The valve body 30 assembled to the housing body 11 through the steps (1) to (5) is pressed to the side opposite to the pressurizing chamber 113 by the disc spring 80 and abuts against the locking member 60. Is locked to the locking member 60.

Next, the difference between the disc spring 80 of this embodiment and the disc spring of a comparative example is demonstrated based on FIG. In FIG. 5, for ease of explanation, the dimensions and shape features of the members are highlighted.
As shown in FIG. 5A, the disc spring 900 of the comparative example is a disc spring having a general shape, and includes only a tapered cylindrical portion 901 having a tapered inner wall and an outer wall. The disc spring 900 is formed by pressing an annular thin plate made of a metal such as stainless steel, for example, like the disc spring 80 of the present embodiment. The disc spring 900 is deformed so that the wall surface constituting the tapered cylindrical portion 901 falls inward when the axial end portions are pressed between the surfaces 501 and 502 and contracted in the axial direction. (See FIG. 5A). At this time, the axial end portion of the tapered cylindrical portion 901 is deformed so as to be crushed by an amount indicated by “deformation amount” in FIG. A cross section of the end portion in the axial direction of the tapered cylindrical portion 901 by a plane including the axis has a substantially right-angled shape. Therefore, the disc spring 900 is deformed so as to be crushed until the axial end portion of the tapered cylindrical portion 901 is in angular contact and reaches the limit surface pressure of the material. It can be said that the disc spring 900 has a relatively small contact width (the contact width between the axial end and the contact surface) with respect to the deformation (the amount of deformation at a location where the axial end is deformed so as to be crushed).

  On the other hand, as shown in FIG. 5C, the disc spring 80 of the present embodiment includes a tapered cylindrical portion 81, an inner flange portion 82, and an outer flange portion 83, and both end portions in the axial direction are, for example, a surface 501 and a surface 502. When pressed in the direction of contracting in the axial direction, the wall surface constituting the tapered cylindrical portion 81 is deformed so as to fall inward. At this time, in the disc spring 80, the boundary portion between the outer flange portion 83 and the tapered tube portion 81 abuts on the surface 501 and the boundary portion between the inner flange portion 82 and the taper tube portion 81 contacts the surface 502 (FIG. 5). (See (C)). As described above, in the present embodiment, the boundary portion between the outer flange portion 83 and the tapered tube portion 81 and the boundary portion between the inner flange portion 82 and the taper tube portion 81 are formed in a relatively smooth curved surface. Yes. It can be said that the disc spring 80 has a relatively large contact width (a width of contact between the axial end portion and the contact surface) with respect to a deformation amount (amount of deformation at a location where the axial end portion is crushed). In the disc spring 80, the surface pressure received from the surface 501 is reduced when the curved boundary portion contacts the surface 501.

  FIG. 6A is a diagram showing the relationship between “surface pressure” and “contact width” received by the axial end portion of the disc spring 900, and the end portion on the surface 501 side of the disc spring 900 is from the surface 501. The relationship between the “surface pressure” received and the “contact width” is indicated by a one-dot chain line, and the relationship between the “surface pressure” and the “contact width” received from the surface 502 by the end of the surface 502 of the disc spring 900 is indicated by a two-dot chain line. Show. FIG. 6B is a diagram showing the relationship between “contact width” and “deformation amount” of the disc spring 80 of the present embodiment and the disc spring 900 of the comparative example formed of the same material. The relationship between the “contact width” and the “deformation amount” of the spring 80 is indicated by a solid line, and the relationship between the “contact width” and the “deformation amount” of the disc spring 900 is indicated by a broken line.

  As can be seen from FIGS. 6A and 6B, the disc spring 900 of the comparative example is a deformation of the end portion on the surface 501 side when the surface pressure received by the end portion on the surface 501 from the surface 501 is “limit surface pressure”. The amount of deformation at the end of the surface 502 side is about 0.054 mm when the amount is about 0.044 mm, and the surface pressure received by the end of the surface 502 from the surface 502 is “limit surface pressure”. The total is about 0.098 mm. On the other hand, in the disc spring 80 of this embodiment, the deformation amount of the surface 501 side end when the surface pressure received by the surface 501 side end from the surface 501 is the “limit surface pressure”, and the surface 502 side end is the surface 502. The deformation amount of the end portion on the side of the surface 502 when the surface pressure received from “the limit surface pressure” is about 0.0005 mm, and the total deformation amount at this time is about 0.001 mm. As described above, the disc spring 80 of the present embodiment has an amount of deformation when the axial end portion receives a predetermined surface pressure (for example, “limit surface pressure”) as compared to the disc spring 900 of the comparative example. Thus, the amount of deformation of the portion to be deformed is small. Thereby, the robustness with respect to the load loss of the disc spring 80 can be improved. However, the characteristics are not limited to the above numerical values.

Next, the operation of the high-pressure pump 10 having the above configuration will be described.
"Inhalation stroke"
When the plunger 13 moves downward in FIG. 2, the energization to the coil 71 is stopped. Therefore, the valve member 40 is urged toward the pressurizing chamber 113 by the needle 49 integral with the movable core 73 receiving the force from the spring 22 of the electromagnetic drive unit 70. As a result, the valve member 40 is separated from the valve seat 34 of the valve body 30. Further, when the plunger 13 moves downward in FIG. 2, the pressure in the pressurizing chamber 113 decreases. Therefore, the force that the valve member 40 receives from the fuel on the concave portion 33 side is larger than the force that is received from the fuel on the pressurization chamber 113 side. As a result, a force is applied to the valve member 40 in a direction away from the valve seat 34, and the valve member 40 is separated from the valve seat 34. The valve member 40 moves until it comes into contact with the cylindrical portion 51 of the stopper 50. When the valve member 40 is separated from the valve seat 34, that is, is opened, the fuel chamber 16 communicates with the pressurizing chamber 113 via the introduction passage 111, the passage 151, and the suction passage 112. Therefore, the fuel in the fuel chamber 16 is sucked into the pressurizing chamber 113 via the first passage 121, the second passage 122, the intermediate passage 124, and the third passage 123 in this order. At this time, the pressure member 113 is covered with the stopper 50 by the valve member 40 being in contact with the stopper 50. Further, at this time, the fuel in the intermediate passage 124 can flow into the volume chamber 54 through the communication passage 55. Therefore, the pressure in the volume chamber 54 is equivalent to the pressure in the intermediate passage 124.

“Weighing process”
When the plunger 13 rises from the bottom dead center toward the top dead center, the flow of fuel discharged from the pressurizing chamber 113 to the valve member 40 side, that is, the fuel chamber 16 side causes the valve member 40 to have a pressure chamber 113 side. A force is applied from the fuel in the direction of seating on the valve seat 34. However, when the coil 71 is not energized, the needle 49 is biased toward the valve member 40 by the biasing force of the spring 22. Therefore, the movement of the valve member 40 toward the valve seat 34 is restricted by the needle 49. Further, the pressure member 113 side of the valve member 40 is covered with a stopper 50. Thereby, the flow of the fuel discharged from the pressurizing chamber 113 to the fuel chamber 16 side does not directly collide with the valve member 40. Therefore, the force in the valve closing direction applied to the valve member 40 by the flow of fuel is alleviated.

  In the metering stroke, the valve member 40 maintains a state of being separated from the valve seat 34 while the energization to the coil 71 is stopped. As a result, the fuel discharged from the pressurizing chamber 113 as the plunger 13 is lifted is opposite to the case where the fuel is sucked into the pressurizing chamber 113 from the fuel chamber 16, the third fuel passage 123, the intermediate passage 124, and the second passage 122. And it returns to the fuel chamber 16 via the 1st channel | path 121 in this order.

  When the coil 71 is energized during the metering process, a magnetic circuit is formed in the fixed core 72, the flange 75, and the movable core 73 by the magnetic field generated in the coil 71. As a result, a magnetic attractive force is generated between the fixed core 72 and the movable core 73 that are separated from each other. When the magnetic attractive force generated between the fixed core 72 and the movable core 73 becomes larger than the urging force of the spring 22, the movable core 73 moves to the fixed core 72 side. Therefore, the needle 49 integrated with the movable core 73 also moves to the fixed core 72 side. When the needle 49 moves to the fixed core 72 side, the valve member 40 and the needle 49 are separated from each other, and the valve member 40 does not receive a force from the needle 49. As a result, the valve member 40 is separated from the stopper 50 by the biasing force of the spring 21 and the force in the valve closing direction applied to the valve member 40 by the flow of fuel discharged from the pressurizing chamber 113 to the fuel chamber 16 side. Move to the seat 34 side. Thereby, the valve member 40 is closed.

  In the present embodiment, the stopper 50 has a communication passage 55 that communicates the intermediate passage 124 and the volume chamber 54 with the cylindrical portion 51. Therefore, the pressure in the volume chamber 54 formed by the inner wall of the cylindrical portion 51 is equal to the pressure in the intermediate passage 124 located on the outer peripheral side of the cylindrical portion 51. That is, even if the pressure in the intermediate passage 124 becomes high, the pressure in the intermediate passage 124 does not become higher than the pressure in the volume chamber 54. Therefore, the valve member 40 can be easily separated from the cylindrical portion 51 of the stopper 50. Thereby, the valve member 40 can be closed at a desired timing.

  When the valve member 40 moves to the valve seat 34 side and the valve member 40 is seated on the valve seat 34, that is, the valve is closed, the second passage 122 is closed and the flow of the fuel flowing through the fuel passage 100 is shut off. . Thus, the metering process for discharging the fuel from the pressurizing chamber 113 to the fuel chamber 16 is completed. When the plunger 13 moves up, the amount of fuel returned from the pressurizing chamber 113 to the fuel chamber 16 is adjusted by closing the second passage 122, that is, between the pressurizing chamber 113 and the fuel chamber 16. As a result, the amount of fuel pressurized in the pressurizing chamber 113 is determined.

"Pressure stroke"
When the plunger 13 further rises toward the top dead center in a state where the pressurizing chamber 113 and the fuel chamber 16 are closed, the fuel pressure in the pressurizing chamber 113 rises. When the pressure of the fuel in the pressurizing chamber 113 becomes equal to or higher than a predetermined pressure, the pressure is reversed against the biasing force of the spring 94 of the discharge valve portion 90 and the force received by the check valve 92 from the fuel downstream of the valve seat 95. The stop valve 92 is separated from the valve seat 95. As a result, the discharge valve section 90 is opened, and the fuel pressurized in the pressurizing chamber 113 is discharged from the high-pressure pump 10 through the discharge passage 114. The fuel discharged from the high-pressure pump 10 is supplied to a delivery pipe (not shown), accumulated, and supplied to the injector.

  When the plunger 13 moves to the top dead center, the energization to the coil 71 is stopped, and the valve member 40 is separated from the valve seat 34 again. At this time, the plunger 13 again moves downward in FIG. 2, and the fuel pressure in the pressurizing chamber 113 decreases. As a result, fuel is sucked into the pressurizing chamber 113 from the fuel chamber 16.

  When the valve member 40 is closed and the fuel pressure in the pressurizing chamber 113 rises to a predetermined value, the energization of the coil 71 may be stopped. When the fuel pressure in the pressurizing chamber 113 rises, the force received in the direction in which the valve member 40 is seated on the valve seat 34 by the fuel on the pressurizing chamber 113 side is greater than the force that the valve member 40 receives in the direction in which the valve member 40 moves away from the valve seat 34. Become. Therefore, even when energization of the coil 71 is stopped, the valve member 40 maintains the seated state on the valve seat 34 by the force received from the fuel on the pressurizing chamber 113 side. Thus, by stopping energization of the coil 71 at a predetermined time, the power consumption of the electromagnetic drive unit 70 can be reduced.

  By repeating the above “intake stroke”, “metering stroke” and “pressurization stroke”, the high pressure pump 10 pressurizes and discharges the sucked fuel. The fuel discharge amount is adjusted by controlling the timing of energizing the coil 71 of the electromagnetic drive unit 70. In the present embodiment, when the high-pressure pump 10 is operated, the “intake stroke”, “metering stroke”, and “pressurization stroke” are repeated, so that the pressure in the pressurizing chamber 113 varies.

  As described above, in this embodiment, the locking member 60 is fitted in the locking groove 153 formed in the housing body 11 and contacts the wall surface of the valve body 30 opposite to the pressurizing chamber 113. The valve body 30 can be locked by contact. Thereby, it is possible to suppress the valve body 30 from coming out to the side opposite to the pressurizing chamber 113. The disc spring 80 is formed in a substantially annular shape, and is provided between the valve body 30 and the annular wall surface 154. The disc spring 80 presses the valve body 30 against the locking member 60 by elastically deforming in the axial direction. Accordingly, the position of the valve body 30 is stabilized in a state where the valve body 30 is in contact with the locking member 60. Therefore, even if the pressure in the pressurizing chamber 113 fluctuates during the operation of the high-pressure pump 10, the valve body 30 can keep its position without being affected by the pressure variation in the pressurizing chamber 113. With this configuration, even if the pressure in the pressurizing chamber 113 varies, variation in the initial position of the needle 49 is suppressed. Therefore, fluctuations in the responsiveness of the valve member 40 are suppressed, and the amount of fuel discharged from the high-pressure pump 10 can be controlled with high accuracy. Moreover, according to this embodiment, since it can suppress that the electromagnetic drive part 70 which attracts | sucks the needle 49, and the needle 49 leave | separate more than predetermined distance, the malfunctioning of the valve member 40 can be suppressed.

  In the present embodiment, since the disc spring 80 presses the valve body 30 against the locking member 60, the locking member 60 is pressed against the wall surface of the locking groove 153. Therefore, it is possible to suppress the backlash between the locking groove 153 and the locking member 60.

  In the present embodiment, the conical passage 301 that connects the inside and the outside of the disc spring 80 is formed on the end surface 38 of the valve body 30 on the disc spring 80 side. As a result, fuel can flow between the inside and outside of the disc spring 80 through the communication path 301, so that the pressure on the inside and the outside of the disc spring 80 can be made the same. Therefore, even if the pressure inside the disc spring 80 fluctuates due to the pressure of the pressurizing chamber 113 fluctuating when the high-pressure pump 10 is operated, the pressure difference between the inside and the outside of the disc spring 80 is suppressed. can do. Therefore, breakage of the disc spring 80 can be suppressed. Therefore, the disc spring 80 can be used for a long time, and the durability of the high-pressure pump 10 can be enhanced.

  Further, in the present embodiment, the disc spring 80 as an elastic member is formed in a circular shape in a radially inward direction from one end portion in the axial direction of the tapered cylindrical portion 81 having a tapered inner wall and an outer wall. The inner flange portion 82 extends, and the outer flange portion 83 extends in an annular shape radially outward from the other axial end of the tapered tube portion 81. The boundary portion between the outer flange portion 83 and the tapered tube portion 81 and the boundary portion between the inner flange portion 82 and the taper tube portion 81 are formed in a relatively smooth curved surface. Thereby, the amount of deformation (the amount of deformation of the portion deformed so as to be crushed) when the axial end portion of the disc spring 80 receives a predetermined surface pressure can be reduced. As a result, the robustness against load loss of the disc spring 80 can be improved.

(Second Embodiment)
A part of the high-pressure pump according to the second embodiment of the present invention is shown in FIG. In FIG. 7, only the valve body of the high-pressure pump according to the second embodiment is shown in order to avoid complication of the drawing. In 2nd Embodiment, the shape of the communicating path formed in a valve body differs from 1st Embodiment.

  As shown in FIGS. 7A and 7B, the end surface 38 on the disc spring 80 (not shown) side of the cylindrical portion 32 of the valve body 30 is formed so as to be recessed toward the opposite side of the disc spring 80. A passage 302 is provided. In the second embodiment, two communication paths 302 are formed. The communication path 302 is formed by linear grooves extending substantially parallel to each other.

  The communication path 302 can communicate the inside and outside of the disc spring 80 with the disc spring 80 in contact with the valve body 30 and the annular wall surface 154 (not shown). That is, a communication passage 302 that connects the inside and the outside of the disc spring 80 is formed on the end surface 38 of the valve body 30 on the disc spring 80 side. In this configuration, when the fuel flows through the communication path 302, the pressures on the inner side and the outer side of the disc spring 80 become substantially the same. The inside of the disc spring 80 and the pressurizing chamber 113 (not shown) are always in communication. Therefore, when the pressure in the pressurizing chamber 113 fluctuates, the pressure inside the disc spring 80 also fluctuates, but the occurrence of a differential pressure between the inside and the outside of the disc spring 80 is suppressed.

(Third embodiment)
A part of the high-pressure pump according to the third embodiment of the present invention is shown in FIG. In FIG. 8, only the valve body of the high-pressure pump according to the third embodiment is shown in order to avoid the figure from becoming complicated. In 3rd Embodiment, the shape of the communicating path formed in a valve body differs from 1st Embodiment.

  As shown in FIGS. 8A and 8B, the end surface 38 on the disc spring 80 (not shown) side of the cylindrical portion 32 of the valve body 30 is formed so as to be recessed toward the opposite side of the disc spring 80. A passage 303 is provided. In the third embodiment, two communication paths 303 are formed. The communication path 303 is configured by forming stepped surfaces that are recessed by a predetermined amount from the end surface 38 at both ends in the radial direction of the end surface 38. That is, it can be said that the communication path 303 has a shape in which the groove-shaped communication path 302 shown in the second embodiment is formed into a stepped surface.

  The communication path 303 can communicate the inside and outside of the disc spring 80 with the disc spring 80 in contact with the valve body 30 and the annular wall surface 154 (not shown). That is, a communication passage 303 that connects the inside and the outside of the disc spring 80 is formed on the end surface 38 of the valve body 30 on the disc spring 80 side. In this configuration, when the fuel flows through the communication path 303, the pressures on the inner side and the outer side of the disc spring 80 become substantially the same. The inside of the disc spring 80 and the pressurizing chamber 113 (not shown) are always in communication. Therefore, when the pressure in the pressurizing chamber 113 fluctuates, the pressure inside the disc spring 80 also fluctuates, but the occurrence of a differential pressure between the inside and the outside of the disc spring 80 is suppressed.

(Fourth embodiment)
A part of the high-pressure pump according to the fourth embodiment of the present invention is shown in FIG. In FIG. 9, only the valve body of the high-pressure pump according to the fourth embodiment is shown in order to avoid the figure from becoming complicated. In 4th Embodiment, the shape of the communicating path formed in a valve body differs from 1st Embodiment.

  As shown in FIG. 9, the end surface 38 of the cylindrical portion 32 of the valve body 30 on the disc spring 80 (not shown) side is provided with a communication passage 304 formed so as to be recessed toward the opposite side of the disc spring 80. . In the fourth embodiment, three communication paths 304 are formed. The communication path 304 is configured by forming step surfaces that are recessed by a predetermined amount from the end surface 38 at three locations in the circumferential direction of the end surface 38. That is, it can also be said that the shape of each communication path 304 is similar to the communication path 303 shown in the third embodiment.

  The communication passage 304 can communicate the inside and outside of the disc spring 80 with the disc spring 80 in contact with the valve body 30 and the annular wall surface 154 (not shown). That is, a communication passage 304 that connects the inside and the outside of the disc spring 80 is formed on the end surface 38 of the valve body 30 on the disc spring 80 side. In this configuration, when the fuel flows through the communication path 304, the pressures on the inside and the outside of the disc spring 80 become substantially the same. The inside of the disc spring 80 and the pressurizing chamber 113 (not shown) are always in communication. Therefore, when the pressure in the pressurizing chamber 113 fluctuates, the pressure inside the disc spring 80 also fluctuates, but the occurrence of a differential pressure between the inside and the outside of the disc spring 80 is suppressed.

(Fifth embodiment)
A part of the high-pressure pump according to the fifth embodiment of the present invention is shown in FIG. In FIG. 10, only the valve body of the high-pressure pump according to the fifth embodiment is shown in order to avoid the figure from becoming complicated. In 5th Embodiment, the shape of the communicating path formed in a valve body differs from 1st Embodiment.

  As shown in FIG. 10, a communication passage 305 formed so as to be recessed toward the opposite side of the disc spring 80 is provided on the end surface 38 of the cylindrical portion 32 of the valve body 30 on the disc spring 80 (not shown) side. . In the fifth embodiment, two communication paths 305 are formed. The communication path 305 is formed by a spiral groove extending so as to connect the outer edge portion and the inner edge portion of the end face 38.

  The communication path 305 can communicate the inside and outside of the disc spring 80 with the disc spring 80 in contact with the valve body 30 and the annular wall surface 154 (not shown). That is, a communication passage 305 that communicates the inside and the outside of the disc spring 80 is formed on the end surface 38 of the valve body 30 on the disc spring 80 side. In this configuration, when the fuel flows through the communication path 305, the pressures on the inner side and the outer side of the disc spring 80 become substantially the same. The inside of the disc spring 80 and the pressurizing chamber 113 (not shown) are always in communication. Therefore, when the pressure in the pressurizing chamber 113 fluctuates, the pressure inside the disc spring 80 also fluctuates, but the occurrence of a differential pressure between the inside and the outside of the disc spring 80 is suppressed.

(Sixth embodiment)
A part of the high-pressure pump according to the sixth embodiment of the present invention is shown in FIG. In 6th Embodiment, the location etc. in which a communicating path is formed differ from 1st Embodiment.

  As shown in FIG. 11, the annular wall surface 154 of the housing body 11 is provided with a communication passage 306 formed so as to be recessed toward the opposite side to the disc spring 80. The communication passage 306 can communicate the inside and the outside of the disc spring 80 in a state where the disc spring 80 is in contact with the valve body 30 and the annular wall surface 154. That is, the annular wall surface 154 is formed with a communication path 306 that communicates the inside and the outside of the disc spring 80. In this configuration, when the fuel flows through the communication path 306, the pressures on the inner side and the outer side of the disc spring 80 become substantially the same. The inside of the disc spring 80 and the pressurizing chamber 113 (not shown) are always in communication. Therefore, when the pressure in the pressurizing chamber 113 fluctuates, the pressure inside the disc spring 80 also fluctuates, but the occurrence of a differential pressure between the inside and the outside of the disc spring 80 is suppressed.

(Seventh embodiment)
A part of the high-pressure pump according to the seventh embodiment of the present invention is shown in FIG. In 7th Embodiment, the location etc. in which a communicating path is formed differ from 1st Embodiment.

  As shown in FIG. 12, a communication passage 307 that connects the inside and the outside of the disc spring 80 is formed in the tapered cylindrical portion 81 of the disc spring 80. Such a disc spring 80 can be easily obtained by, for example, forming a hole connecting one end surface and the other end surface in an annular thin plate to form a communication path 307 and then pressing the thin plate. Can be manufactured.

  In the above configuration, when the fuel flows through the communication path 307, the pressures on the inner side and the outer side of the disc spring 80 become substantially the same. The inside of the disc spring 80 and the pressurizing chamber 113 (not shown) are always in communication. Therefore, when the pressure in the pressurizing chamber 113 fluctuates, the pressure inside the disc spring 80 also fluctuates, but the occurrence of a differential pressure between the inside and the outside of the disc spring 80 is suppressed.

(Eighth embodiment)
A part of the high-pressure pump according to the eighth embodiment of the present invention is shown in FIG. In the eighth embodiment, the shape and the like of the elastic member are different from those in the first embodiment.

  As shown in FIG. 13, in the eighth embodiment, a wave spring 85 as an elastic member is provided between the valve body 30 and the annular wall surface 154. Like the disc spring 80 of the first embodiment, the wave spring 85 generates an elastic force in the axial direction in a state where it is provided between the valve body 30 and the annular wall surface 154 so that the valve body 30 is engaged with the locking member 60 ( (Not shown).

  The wave spring 85 can be said to have a communication passage 308 that communicates the inside and the outside of the wave spring 85 in a state where both end portions in the axial direction are in contact with the valve body 30 and the annular wall surface 154 due to its shape. . That is, a plurality of communication passages 308 (gap) are formed between the wave spring 85 and the end surface 38 of the valve body 30 and between the wave spring 85 and the annular wall surface 154.

  In this configuration, when the fuel flows through the communication path 308, the pressure on the inner side and the outer side of the wave spring 85 becomes substantially the same. The inside of the wave spring 85 and the pressurizing chamber 113 (not shown) are always in communication. Therefore, when the pressure in the pressurizing chamber 113 fluctuates, the pressure inside the wave spring 85 also fluctuates, but the occurrence of a differential pressure between the inside and the outside of the wave spring 85 is suppressed. Therefore, breakage of the wave spring 85 can be suppressed. Therefore, the wave spring 85 can be used over a long period of time, and the durability of the high pressure pump can be enhanced.

  As described above, when the wave spring 85 is used as the elastic member, it is separately connected to at least one of the elastic member side end surface, the annular wall surface 154 and the elastic member of the valve body 30 as in the first to seventh embodiments. There is no need to provide a passage. Therefore, the manufacturing cost can be reduced while improving the durability of the high-pressure pump.

(Other embodiments)
In another embodiment of the present invention, the elastic member may be formed in any shape as long as it is formed in a substantially annular shape and can have an elastic force in the axial direction.

  In the above-described embodiment, the example in which the communication path that connects the inner side and the outer side of the elastic member is formed in any one of the elastic member side end surface, the annular wall surface, and the elastic member of the valve body has been described. On the other hand, in other embodiment of this invention, it is good also as forming a communicating path in multiple places among the elastic member side end surface of a valve body, an annular wall surface, and an elastic member. Or it is good also as a structure which does not provide one such communication path.

  In the above-described eighth embodiment, since the wave spring is used as the elastic member and the wave spring itself has a communication path, no separate communication path is formed on the elastic member (wave spring) side end surface or the annular wall surface of the valve body. An example is shown. On the other hand, in another embodiment of the present invention, even when a wave spring is used as the elastic member, a separate communication path is provided on at least one of the end surface of the valve body on the elastic member (wave spring) side and the annular wall surface. Also good.

  In another embodiment of the present invention, the shape of the locking groove formed in the housing is not limited to an annular shape as long as the locking member can be fitted, and may have any shape. The locking member may have any shape and number as long as the valve body can be locked by being fitted in the locking groove. Further, the locking member may be provided integrally with the housing. For example, the valve body may be locked by a protruding portion that is formed so as to protrude radially inward from the passage wall surface of the housing.

  In the above-described embodiment, an example in which the valve member and the needle are configured separately has been described. On the other hand, in another embodiment of the present invention, the valve member and the needle may be connected and integrally formed.

In the above-described embodiment, the normally open type valve structure is shown in which the valve member is opened when the coil portion of the electromagnetic drive portion is not energized, and the valve member is closed when the coil portion is energized. On the other hand, in another embodiment of the present invention, a normally closed valve structure in which the valve member opens when the coil portion is energized may be used.
Thus, the present invention is not limited to the above-described embodiment, and can be applied to various embodiments without departing from the scope of the invention.

  10: high-pressure pump, 11: housing body (housing), 13: plunger, 113: pressurizing chamber, 151: passage (fuel passage), 152: passage wall surface, 153: locking groove, 154: annular wall surface, 21: spring (First urging member), 22: spring (second urging member), 30: valve body, 34: valve seat, 40: valve member, 49: needle, 60: locking member, 70: electromagnetic drive unit, 71: coil (coil part), 72: fixed core (coil part), 73: movable core (coil part), 75: flange (coil part), 78: spool (coil part), 79: cylindrical member (coil part) , 80: disc spring (elastic member), 85: wave spring (elastic member)

Claims (1)

A reciprocating plunger; and
A pressurizing chamber in which fuel is pressurized by the plunger, a substantially cylindrical passage wall surface that forms a fuel passage that guides fuel to the pressurizing chamber, a locking groove that is recessed radially outward of the passage wall surface, and the engagement A housing having an annular wall surface extending in the radial direction of the passage wall surface between the stop groove and the pressurizing chamber and formed in a substantially annular shape;
A valve body provided on the opposite side of the annular wall from the pressurizing chamber, and having a valve seat on the wall of the pressurizing chamber;
A valve member that interrupts the flow of fuel flowing through the fuel passage by being seated on or separated from the valve seat;
A first biasing member that is provided on the pressure chamber side of the valve member and biases the valve member in a valve closing direction;
The valve member is provided so as to be in contact with or connected to the end opposite to the pressurizing chamber, and is movable in the same direction as the valve member when the valve member is opened or closed. Needle,
A second biasing member that biases the needle in the valve opening direction of the valve member;
An electromagnetic drive unit having a coil unit capable of attracting the needle in either the valve closing direction or the valve opening direction of the valve member;
A locking member that is fitted in the locking groove and that can lock the valve body by contacting the wall surface of the valve body opposite to the pressurizing chamber;
A substantially annular elastic member that is provided between the valve body and the annular wall surface and that elastically deforms in the axial direction to press the valve body against the locking member ;
At least one of the elastic member side end surface, the annular wall surface, and the elastic member of the valve body is formed with a communication path that connects the inside and the outside of the elastic member,
The elastic member is a disc spring, a tapered cylindrical portion having a tapered inner wall and an outer wall, an inner flange portion extending in an annular shape radially inward from one axial end portion of the tapered cylindrical portion, and An outer flange portion extending in an annular shape radially outward from the other axial end of the tapered tube portion;
A boundary portion between the outer flange portion and the tapered cylinder portion, and a boundary portion between said inside flange portion and the tapered tube portion, the high-pressure pump, characterized that you have been formed into a curved shape.

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