JP2017053419A - Seal member and high pressure pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a seal member capable of restricting stress applied to both ends in an axial direction due to tolerance or thermal expansion, restricting axial motion in a seal groove and assuring a stable contact state between it and an outer peripheral surface of a shaft member.SOLUTION: A seal member 15 has an annular seal main body 28 installed in seal grooves 24 formed at opposing positions of a plunger 5, an inner peripheral surface 28b is contacted with an outer peripheral surface of the plunger 5 and an outer peripheral surface 28a is contacted with a groove bottom surface 241. The seal main body 28 has inner lip portions 28d protruded from an intermediate part 28c and from radial inner sides at both ends of the intermediate part 28c and an outer lip part 28f protruded from outside in a radial direction in an axial direction. An extremity end of the outer lip part 28f is formed with a clashing margin setting part 28k contacted with groove side surfaces 242, 243 while keeping clashing margin. The clashing margin setting part 28k is formed into a protrusion shape that is deformed inside in a radial direction. The inner lip portions 28d are arranged under no contacted state with the groove side surfaces 242, 243.SELECTED DRAWING: Figure 2

Description

  The present invention is attached to an annular seal groove formed at a position opposite to the outer peripheral surface of a reciprocating shaft member, and suppresses leakage of a medium from one side to the other side in the axial direction from the seal groove. The present invention relates to a member and a high pressure pump including the seal member.

  2. Description of the Related Art Conventionally, a high-pressure pump that is provided in a fuel supply system that supplies fuel to an internal combustion engine and that feeds fuel under pressure is known. The high-pressure pump sucks fuel from the supply passage into the pressurizing chamber and pressurizes it by reciprocating movement of the plunger accommodated in the cylinder. There is also known a high-pressure pump in which a plunger reciprocates by rotation of a camshaft of an internal combustion engine.

  In this type of high-pressure pump, it is necessary to suppress the leakage of fuel from the clearance between the plunger and the cylinder to the internal combustion engine and to suppress the intrusion of engine oil from the internal combustion engine into the high-pressure pump. When fuel leaks from the high-pressure pump to the internal combustion engine, the fuel is mixed into the engine oil, and there is a concern about deterioration of lubrication and fuel consumption of the internal combustion engine. On the other hand, when engine oil is mixed into the high-pressure pump from the internal combustion engine, there is a concern that the properties of the fuel discharged from the high-pressure pump deteriorate.

  Therefore, normally, a sliding member between the plunger and the cylinder is provided with a seal member that suppresses leakage of a medium (fuel or engine oil) from one side in the axial direction to the other side. The seal member is formed in an annular shape and is provided in an annular seal groove formed at a position facing the outer peripheral surface of the plunger (see, for example, Patent Document 1). The inner peripheral surface and the outer peripheral surface of the annular seal member are in liquid-tight contact with the outer peripheral surface of the plunger and the bottom surface (groove bottom surface) of the seal groove. Further, in Patent Document 1, when an elastic protruding piece is protruded from the tip of the inner peripheral lip portion formed on the radially inner side of the seal member toward the side surface of the seal groove, and the seal member is attached to the seal groove. A configuration is described in which the elastic protrusion is brought into contact with the side surface of the seal groove in a bent state.

Japanese Patent No. 4705138

  By the way, the seal member needs to be provided so as not to come out of the seal groove. In order to prevent the seal member from coming off, a method of fixing both ends of the seal member in the axial direction to the side surface of the seal groove is conceivable. However, in this method, there is a concern that stress is applied to both ends of the seal member due to tolerance or thermal expansion of the seal member, and the shape of the seal member is deformed by the stress, and the sealing performance is deteriorated. In order to prevent stress from being applied to both ends, it is conceivable to provide a sufficient gap between the end portion in the axial direction of the seal member and the side surface of the seal groove. However, in this case, the reciprocating movement of the shaft member may cause the seal member to move in the axial direction within the seal groove, which may cause the seal member to wear or change its shape. In particular, since it is not assumed that the outer peripheral surface of the seal member that contacts the bottom surface of the seal groove is slid, there is a concern about wear of the outer peripheral surface.

  In this regard, according to the seal member of Patent Document 1, the elastic protrusions protruding from the tip of the inner peripheral lip are brought into contact with the side surfaces of the seal groove in a bent state, so that the stress applied to both ends is absorbed. It is possible to suppress the movement of the seal member in the seal groove. However, in the configuration of Patent Document 1, there is a concern that the elastic force by the elastic protrusions affects the contact state between the inner peripheral surface of the seal member and the outer peripheral surface of the shaft member.

  The present invention has been made in view of the above circumstances, can suppress stress on both ends in the axial direction due to tolerance and thermal expansion, can be prevented from moving in the axial direction in the seal groove, and It is an object of the present invention to provide a seal member that can ensure a stable contact state with the outer peripheral surface of the member, and a high-pressure pump including the seal member.

In order to solve the above problems, a seal member of the present invention is a seal member provided in an annular seal groove formed at a position facing an outer peripheral surface of a shaft, which is an outer peripheral surface of a shaft member that reciprocates in the axial direction. ,
An inner peripheral surface that is in contact with the outer peripheral surface of the shaft so as to suppress leakage of the medium from one side of the seal groove to the other side in the axial direction, and a surface of the seal groove that faces the outer peripheral surface of the shaft. An annular seal body having an outer peripheral surface in contact with a certain groove bottom;
A surface facing the axial direction of the seal groove as a groove side surface,
The seal body has a crushing margin setting portion that contacts a side surface of the groove with a crushing margin at a position radially outside at least one of both ends in the axial direction.

  According to the present invention, since at least one of both ends in the axial direction of the seal body has the crushing allowance setting portion that contacts the side surface of the groove with crushing allowance, the seal member moves in the axial direction in the seal groove. While being able to suppress, the change in the shape of the seal member due to tolerance or thermal expansion can be absorbed by the crushing margin set in the crushing margin setting section. Therefore, it can suppress that stress is applied to both ends, and it can control that the shape of a seal member changes with the stress. Furthermore, since the crushing margin setting part is formed at a position on the radially outer side, it is possible to suppress the elastic force of the crushing margin setting part from affecting the inner peripheral surface (radially inner side) of the seal member. Therefore, a stable contact state can be secured between the inner peripheral surface of the seal body and the outer peripheral surface of the shaft member.

The high-pressure pump of the present invention is
A plunger,
A cylinder in which the plunger is reciprocally movable in an axial direction and slidably accommodated, and a cylinder having an annular seal groove formed at a position facing the outer peripheral surface of the plunger;
A suction valve portion for opening and closing a liquid suction port to a pressurizing chamber formed between an end surface of the plunger and an inner wall surface of the cylinder;
A discharge valve provided in a discharge passage for discharging the liquid pressurized in the pressurizing chamber, and opening and closing the discharge passage;
A seal member of the present invention provided in the seal groove;
Is provided.

  According to the high-pressure pump of the present invention, the same effect as that of the sealing member can be obtained.

It is principal part sectional drawing of a high pressure pump. It is an enlarged view of the A section of FIG. 1 in 1st Embodiment. It is an enlarged view of the A section of FIG. 1 in 2nd Embodiment. It is an enlarged view of the A section of FIG. 1 in 3rd Embodiment. It is an enlarged view of the A section of FIG. 1 in 4th Embodiment. It is an enlarged view of the A section of FIG. 1 in 5th Embodiment. It is an enlarged view of the A section of FIG. 1 in 6th Embodiment. It is an enlarged view of the A section of FIG. 1 in 7th Embodiment. It is an enlarged view of the A section of FIG. 1 in 8th Embodiment. It is an enlarged view of the A section of FIG. 1 in 9th Embodiment.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. A high-pressure pump 100 shown in FIG. 1 is used by being mounted on a vehicle, pressurizes fuel supplied from a fuel tank by a low-pressure pump (feed pump), and discharges the fuel to a common rail to which an injector is connected. The high-pressure fuel stored in the common rail is injected into a cylinder of an internal combustion engine (diesel engine). A pipe from the low pressure pump is connected to the upstream side of the fuel inlet of the high pressure pump 100.

  The high-pressure pump 100 includes a cylinder 3 that forms an outer shell. Inside the cylinder 3, a cylindrical storage chamber 16 (cylinder) formed in a shape extending in the vertical direction of FIG. 1 is formed. A rod-like plunger 5 is accommodated in the accommodation chamber 16 so as to be reciprocable in the direction of the axis L1 (see FIG. 2) of the plunger 5 (hereinafter referred to as the axial direction) and slidable with respect to the wall surface of the accommodation chamber 16. Yes. In addition, the outer peripheral surface of the plunger 5 and the wall surface of the storage chamber 16 are not completely in contact with each other, and a minute gap (a gap of about several μm) is formed.

  The plunger 5 is connected to a large-diameter portion 51 provided on the pressurizing chamber 17 side and an end surface on the opposite side of the end surface 53 of the large-diameter portion 51 on the pressurizing chamber 17 side, and has a small diameter smaller than that of the large-diameter portion 51. Part 52. The large diameter part 51 and the small diameter part 52 are formed coaxially. A part of the small diameter portion 52 and the large diameter portion 51 are disposed in a recess 121 formed in the engine block 12. Specifically, the engine block 12 is formed with a recess 121 that is recessed to a position facing the camshaft 13 of the internal combustion engine. A part 31 of the cylinder 3 is formed in a convex shape that fits into the recess 121. A part of the large-diameter portion 51 and the small-diameter portion 52 are provided so as to protrude from the end portion of the storage chamber 16 formed in the convex portion 31 of the cylinder 3 to the camshaft 13 side. The plunger 5 corresponds to a shaft member.

  A cam 14 is connected to the camshaft 13. The cam 14 is provided at a position facing the recess 121. A roller 9 is provided on the plunger 5 side from the cam 14 so as to be slidable with respect to the surface of the cam 14 and movable up and down in accordance with the rotation state (cam profile) of the cam 14. The roller 9 is supported by a pin 10 and a bush 11. A tappet body 8 is provided between the plunger 5 and the roller 9 in the recess 121 so as to be movable in the direction from the cam 14 toward the plunger 5 and in the opposite direction (that is, the vertical direction in FIG. 1). The tappet body 8 is formed in an H-shaped cross-sectional shape in the cross-sectional view of FIG. Specifically, the tappet body 8 includes a side surface 81 that is provided so as to slide on the inner wall of the recess 121, a lower recess 82 that is recessed from the end surface on the cam 14 side toward the plunger 5, and the cam 14 from the end surface on the plunger 5 side. And an upper recess 83 that is recessed to the side. The roller 9 is disposed in the lower recess 82.

  The small diameter portion 52 is provided in the upper concave portion 83. The end portion 54 of the small diameter portion 52 is provided in contact with the bottom surface of the upper concave portion 83. In addition, the lower sheet 7 is disposed in the upper concave portion 83 so as to be in contact with the stepped surface formed in the end portion 54. The end portion 54 is urged toward the bottom surface side (the cam 14 side) of the upper concave portion 83 by the plunger spring 6 through the lower seat 7. That is, the plunger 5 is constantly biased toward the cam 14 side.

  When the roller 9 moves to the plunger 5 side by the rotation of the cam 14, the roller 9 comes into contact with the bottom surface of the lower recess 82, and the tappet body 8 moves to the plunger 5 side. By the movement, the plunger 5 moves upward against the urging force of the plunger spring 6. On the other hand, when the roller 9 moves to the cam 14 side by the rotation of the cam 14 and moves away from the bottom surface of the lower recess 82, the plunger 5, the lower seat 7 and the tappet body 8 are moved to the cam 14 side by the biasing force of the plunger spring 6. Moving. Thus, the plunger 5 reciprocates in the axial direction by the rotation of the cam 14.

  The pressurizing chamber 17 is formed so as to face the upper end surface 53 of the plunger 5. The pressurizing chamber 17 is a space formed between the end surface 53 and the inner wall of the cylinder 3. The pressurizing chamber 17 is a space whose volume is changed by the reciprocating movement of the plunger 5.

  The high-pressure pump 100 includes an intake valve portion 1 that controls intake of fuel into the pressurizing chamber 17. A supply passage 21 is formed in the cylinder 3 to guide the fuel supplied from the low pressure pump to the fuel inlet to the intake valve portion 1. In the present embodiment, the suction valve portion 1 is disposed outside the pressurizing chamber 17 in the axial direction of the plunger 5, but may be disposed outside in the radial direction.

  The suction valve unit 1 includes a cylindrical valve body 18, a suction valve 19, a needle 20, and an electromagnetic valve 2. A through hole communicating with the pressurizing chamber 17 is formed in the valve body 18, and a suction valve 19 is disposed in the through hole. A tapered seat portion 181 is formed at the opening of the through hole of the valve body 18. The front end portion 191 of the suction valve 19 is disposed on the seat portion 181. The valve body 18 is formed with a suction chamber 22 to which a supply passage 21 is connected. The suction chamber 22 communicates with the pressurization chamber 17 through a through hole in which the suction valve 19 is disposed. A rod-like needle 20 is in contact with the end of the intake valve 19 opposite to the tip 191. The needle 20 extends to the inside of the electromagnetic valve 2.

  The electromagnetic valve 2 is a part that drives the needle 20 in the axial direction. Specifically, the electromagnetic valve 2 includes a coil, a spring, a fixed core, and a movable core. The movable core is fixed integrally with the needle 20. When the coil is energized, a magnetic attractive force is generated between the fixed core and the movable core. As a result, the movable core moves toward the fixed core, and accordingly, the needle 20 moves away from the pressurizing chamber 17. At this time, since the movement of the suction valve 19 is not restricted by the needle 20, the suction valve 19 is seated on the seat portion 181. The suction chamber 22 and the pressurization chamber 17 are blocked by the seating of the suction valve 19.

  On the other hand, if the coil is not energized, no magnetic attractive force is generated, and therefore the movable core and the needle 20 are moved toward the pressurizing chamber 17 by the spring. The needle 20 holds the suction valve 19 on the pressurizing chamber 17 side. As a result, the suction valve 19 is separated from the seat portion 181, and the suction chamber 22 and the pressurizing chamber 17 communicate with each other.

  A discharge passage 23 is formed on the radially outer side of the pressurizing chamber 17 so as to communicate with the pressurizing chamber 17. A discharge valve 4 is disposed in the discharge passage 23. The discharge valve 4 includes a ball portion that can open and close the discharge passage 23 and a spring that biases the ball portion in a direction to close the discharge passage 23. The discharge valve 4 opens when the force acting on the fuel pressure in the pressurizing chamber 17 becomes larger than the force acting on the discharge valve 4 and the biasing force of the spring from the downstream side of the discharge valve 4. When the discharge valve 4 is opened, the pressurizing chamber 17 and the discharge passage 23 are opened, and the fuel pressurized in the pressurizing chamber 17 flows through the discharge passage 23 and is discharged from the fuel discharge port.

  A part of the fuel sucked into the pressurizing chamber 17 may flow toward the small diameter portion 52 through a gap between the outer peripheral surface of the plunger 5 and the inner wall surface of the cylinder 3 (accommodating chamber 16). In order to prevent the overflow fuel flowing through the gap between the outer peripheral surface of the plunger 5 and the inner wall surface of the cylinder 3 from leaking to the internal combustion engine side, a recovery passage for guiding the overflow fuel to the OF fuel outlet in the cylinder 3 25 is formed. The recovery passage 25 is formed so as to communicate with an upper side surface (side surface on the pressurizing chamber 17 side) of a seal groove 24 described later.

  The high pressure pump 100 includes a seal member 15. Details of the seal member 15 will be described later.

  Next, the operation of the high-pressure pump 100 will be described. When the plunger 5 is lowered from the top dead center toward the bottom dead center by the rotation of the cam 14, the volume of the pressurizing chamber 17 increases and the fuel is depressurized. The discharge valve 4 is closed by this pressure reduction. At this time, energization to the coil of the electromagnetic valve 2 is stopped, and the suction valve 19 maintains the open state. Thereby, fuel is sucked into the pressurizing chamber 17 from the suction chamber 22 (suction process).

  When the plunger 5 rises from the bottom dead center toward the top dead center due to the rotation of the cam 14, the volume of the pressurizing chamber 17 decreases. At this time, energization to the coil of the solenoid valve 2 is stopped until a predetermined time, and the suction valve 19 is in an open state. For this reason, the low-pressure fuel once sucked into the pressurizing chamber 17 is returned to the suction chamber 22. By starting energization of the coil at a predetermined time while the plunger 5 is rising, the intake valve 19 is closed (metering step).

  After the intake valve 19 is closed, the fuel pressure in the pressurizing chamber 17 increases as the plunger 5 rises. When the force that the fuel pressure in the pressurizing chamber 17 acts on the discharge valve 4 becomes larger than the force that the fuel pressure from the downstream side of the discharge valve 4 acts on the discharge valve 4 and the biasing force of the spring that acts on the discharge valve 4. Valve 4 opens. Thereby, the fuel pressurized in the pressurization chamber 17 is discharged from a fuel discharge port (pressurization process).

  As described above, the high-pressure pump 100 pressurizes and discharges the sucked fuel by repeating the suction process, the metering process, and the pressurization process. In the metering step, the fuel discharge amount can be adjusted by adjusting the timing for closing the intake valve 19.

  Here, a part of the high-pressure pump 100 (a mechanism part for reciprocating the plunger 5) is disposed in the engine block 12 (recessed part 121). The engine block 12 is in an environment of engine oil, and the portion of the high-pressure pump 100 that is disposed in the recess 121 is oil-lubricated with engine oil. Thereby, the lubricity of a mechanism portion for reciprocating the plunger 5 such as a sliding portion between the roller 9 and the cam 14 is ensured.

  Thus, since a part of high-pressure pump 100 exists in an oil environment, there exists a possibility that engine oil may leak into the high-pressure pump 100 (pressure chamber 17 side). On the other hand, the portion of the high-pressure pump 100 where the pressurizing chamber 17, the intake valve portion 1 and the like are formed is in a fuel environment, and there is a concern that the fuel leaks to the internal combustion engine side. In particular, leakage of fuel and engine oil is performed through a gap between the plunger 5 and the inner wall surface of the cylinder 3 (accommodating chamber 16). In order to suppress such leakage, the high-pressure pump 100 is provided with a seal member 15. Details of the seal member 15 will be described below.

  The seal member 15 is disposed so as to surround the outer peripheral portion of the large-diameter portion 51 at a position in the vicinity of the end portion of the large-diameter portion 51 of the plunger 5 opposite to the pressurizing chamber 17 (hereinafter referred to as a lower end portion). ing. Specifically, an annular seal groove 24 is formed in the cylinder 3 at a position slightly above the lower end of the large diameter portion 51 and at a position facing the outer peripheral surface of the large diameter portion 51. More specifically, a small-diameter convex portion 32 (see FIG. 2) is formed on the lower end side of the convex portion 31 of the cylinder 3 disposed in the engine block 12. The small-diameter convex portion 32 is formed with a concave portion 32a that is recessed from the lower end surface 33 to the upper side in the axial direction (the pressurizing chamber 17 side). A cover member 26 is attached to the small-diameter convex portion 32.

  As shown in FIG. 2, the cover member 26 includes a first tubular portion 261 having an inner diameter equivalent to the outer diameter of the small-diameter convex portion 32 and an end disposed on the cam 14 side of the first tubular portion 261. And a second cylindrical part 262 having an inner diameter smaller than the inner diameter of the first cylindrical part 261. The inner peripheral surface of the first cylindrical portion 261 and the inner peripheral surface of the second cylindrical portion 262 are connected via a step surface 243 formed perpendicular to the axial direction. The inner peripheral surface of the first tubular portion 261 and the outer peripheral surface of the small-diameter convex portion 32 are in contact with each other. Further, the inner diameter of the second cylindrical portion 262 is set to a value larger than the diameter of the plunger 5. Thereby, a gap 27 is formed between the inner peripheral surface of the second cylindrical portion 262 and the outer peripheral surface of the plunger 5. The gap 27 is larger than the gap between the inner wall surface of the cylinder 3 and the outer peripheral surface of the plunger 5. The lower end surface 33 of the small-diameter convex portion 32 is in contact with the step surface 243. A part of the step surface 243 on the inner diameter side is not in contact with the lower end surface 33, that is, is exposed when viewed from the inside of the recess 32a.

  The seal groove 24 includes a recess 32 a and a part of the exposed step surface 243. The seal groove 24 is directed to the outer peripheral surface 55 of the plunger 5 (in other words, formed in parallel to the outer peripheral surface 55), and both side surfaces standing radially inward from both axial ends of the bottom surface 241. 242 and 243. The side surfaces 242 and 243 are formed in a shape facing the axial direction of the plunger 5 (in other words, an angle perpendicular to the outer peripheral surface 55). A cross-sectional line of the bottom surface 241 when the seal groove 24 is cut along a plane perpendicular to the axial direction is circular.

  The seal member 15 is formed in a rotationally symmetric shape with respect to a predetermined axis L2, and specifically, formed in an annular shape (in other words, a cylindrical shape) having an insertion hole 28b of the plunger 5 on the inner side. Further, the seal member 15 is formed in a symmetrical shape with respect to a plane 200 (see FIG. 2) perpendicular to the axial direction (the direction of the central axis L2 of the seal body 28). The seal member 15 is press-fitted into the seal groove 24 in a form in which the plunger 5 is inserted into the insertion hole 28b. The seal member 15 includes a seal body 28 that constitutes an outline of the seal member 15 and a spring 29.

  The seal body 28 is formed of a resin such as PTFE (polytetrafluoroethylene) that can exhibit a sealing function. The seal body 28 has a rotationally symmetric shape with respect to the axis L2, and is formed in an annular shape (in other words, a cylindrical shape) having an outer peripheral surface 28a and an inner peripheral surface 28b (an insertion hole for the plunger 5). The seal body 28 is disposed in the seal groove 24 such that the inner peripheral surface 28 b is slidably in contact with the outer peripheral surface 55 of the plunger 5 and the outer peripheral surface 28 a is in contact with the groove bottom surface 241. At this time, the center axis L2 of the seal body 28 coincides with the axis L1 of the plunger 5. Hereinafter, the direction of the central axis L2 is referred to as the axial direction of the seal member 15 (seal main body 28), and the direction perpendicular to the axial direction is referred to as the radial direction.

  Specifically, the seal main body 28 includes an intermediate portion 28c positioned in the middle in the axial direction, and a lip portion provided so as to protrude in the axial direction from an end portion in the axial direction of the intermediate portion 28c. The lip portion includes an inner lip portion 28d formed radially inward at the axial end of the intermediate portion 28c, and an outer lip portion 28f formed radially outward. Further, the inner lip portion 28d includes a lip portion 281 that protrudes upward in the axial direction (direction toward the pressurizing chamber 17 side) from the upper end portion (end portion on the pressurizing chamber 17 side) of the intermediate portion 28c, and the intermediate portion 28c. A lip portion 282 protruding downward in the axial direction (direction on the cam 14 side) from the lower end portion (end portion on the cam 14 side). Similarly, the outer lip portion 28f includes a lip portion 283 that protrudes upward in the axial direction from the upper end portion of the intermediate portion 28c, and a lip portion 284 that protrudes downward in the axial direction from the lower end portion of the intermediate portion 28c.

  The upper and lower lip portions 281 and 282 (inner lip portion 28d) formed on the radially inner side are formed symmetrically with respect to a plane set at a right angle to the axial direction. The inner lip portion 28d is formed to be continuous over the entire circumference in the circumferential direction of the seal body 28, that is, formed in an annular shape. The inner peripheral surface of the inner lip portion 28d constitutes a part of the inner peripheral surface 28b of the seal body 28. An inward lip portion 28e protruding inward in the radial direction is formed on the inner peripheral surface of the inner lip portion 28d. The inward lip portion 28e is formed to be continuous over the entire circumference of the seal body 28 in the circumferential direction. The inward lip portion 28 e is in contact with the outer peripheral surface 55. At this time, the inclination angle of the inward lip portion 28e (the inclination angle from the tip of the inner lip portion 28d to the apex of the inward lip portion 28e and the inner lip so that medium leakage through the inward lip portion 28e is suppressed. The inclination angle from the root of the portion 28d toward the apex of the inward lip portion 28e) is set to a predetermined value.

  The width in the radial direction of the inner lip portion 28d is smaller than the width in the radial direction of the intermediate portion 28c. Further, the length of the inner lip portion 28d in the axial direction is shorter than the length of the outer lip portion 28f in the axial direction (a length including a crush margin setting portion 28k described later). That is, a gap is formed between the inner lip portion 28d and the groove side surfaces 242 and 243. The gap is set to a sufficiently large value so that the inner lip portion 28d and the groove side surfaces 242 and 243 do not contact even if the shape of the seal body 28 changes due to tolerance or thermal expansion. Thus, the inner lip portion 28d is provided in a non-contact state on the groove side surfaces 242 and 243.

  The inner peripheral surface 28b of the seal body 28 is in contact with the outer peripheral surface 55 only by the inward lip portion 28e. That is, the inner concave surface 28h which is a portion other than the inward lip portion 28e in the inner peripheral surface 28b is formed to be recessed outward in the radial direction from the inward lip portion 28e. For this reason, the inner concave surface 28 h is not in contact with the outer peripheral surface 55 and forms a gap with the outer peripheral surface 55. The inner concave surface 28h is formed between an inward lip portion 28e formed on the upper inner lip portion 281 and an inward lip portion 28e formed on the lower inner lip portion 282.

  In this way, by contacting the outer peripheral surface 55 only with the inward lip portion 28e, the gradient of the seal surface pressure can be easily increased as compared with the configuration in which the entire inner peripheral surface is in contact with the outer peripheral surface 55, and the medium leaks. Can be effectively suppressed. Further, by forming a gap between the inner peripheral surface 28h (inner concave surface) between the upper and lower inward lip portions 28e and the outer peripheral surface 55, the medium temporarily enters the gap through one inward lip portion 28e. Even if it flows in, it can suppress that the internal peripheral surface 28h gets wet with a medium, and it can suppress that the medium which flowed into the clearance gap leaks from the other inward lip part 28e to the opposite side.

  Further, the distance between the upper and lower inward lip portions 28 e is set to a distance longer than the movement amount of the plunger 5. As a result, even if the medium flows into the gap between the inner concave surface 28h and the outer peripheral surface 55 when the plunger 5 is raised or lowered, the medium leaks from the opposite inward lip 28e to the opposite region. Can be suppressed.

  On the other hand, the upper and lower lip portions 283 and 284 (outer lip portion 28f) formed on the outer side in the radial direction are also formed in a symmetrical shape with respect to a plane set at a right angle in the axial direction. The outer lip portion 28f is formed in a shape that is continuous over the entire circumference in the circumferential direction of the seal body 28, that is, formed in an annular shape. The outer peripheral surface of the outer lip portion 28 f constitutes a part of the outer peripheral surface 28 a of the seal body 28. An outward lip portion 28g protruding outward in the radial direction is formed on the outer peripheral surface of the outer lip portion 28f. The outward lip portion 28g is formed to be continuous over the entire circumference of the seal body 28 in the circumferential direction. The outward lip portion 28 g is in contact with the groove bottom surface 241. The inclination angle of the outward lip portion 28g is set to the same inclination angle as that of the inward lip portion 28e.

  The width of the outer lip portion 28f in the radial direction is smaller than the width of the intermediate portion 28c in the radial direction. The length and tip shape of the outer lip portion 28f in the axial direction will be described later.

  The outer peripheral surface 28a of the seal body 28 is in contact with the groove bottom surface 241 only by the outward lip portion 28g. That is, the outer concave surface 28i, which is a portion other than the outward lip portion 28g in the outer peripheral surface 28a, is formed to be recessed inward in the radial direction from the outward lip portion 28g. For this reason, the outer concave surface 28 i is not in contact with the groove bottom surface 241 and forms a gap with the groove bottom surface 241. The outer concave surface 28i is formed between an outward lip portion 28g formed on the upper outer lip portion 283 and an outward lip portion 28g formed on the lower outer lip portion 284.

  Thereby, it is possible to easily increase the gradient of the seal surface pressure, and it is possible to effectively suppress the leakage of the medium. Further, by forming a gap between the outer peripheral surface 28i (outer concave surface) between the upper and lower outward lip portions 28g and the groove bottom surface 241, the medium temporarily flows into the gap via one outward lip portion 28g. Even if it does, it can suppress that the outer peripheral surface 28i gets wet with a medium, and can suppress that the medium which flowed into the clearance gap leaks to the other side from the other outward lip | rip part 28g.

  Further, the distance between the upper and lower outward lip portions 28g is set to a distance longer than the movement amount of the plunger 5. As a result, even if the medium flows into the gap between the outer concave surface 28i and the groove bottom surface 241 when the plunger 5 is raised or lowered, the medium leaks from the opposite outward lip portion 28g to the opposite region. Can be suppressed.

  The inner peripheral surface and the outer peripheral surface of the intermediate portion 28c constitute the inner concave surface 28h and the outer concave surface 28i described above. That is, lip portions are not formed on the inner peripheral surface and the outer peripheral surface of the intermediate portion 28c.

  Further, the inner lip 281 and the outer lip 283 formed on the upper side are formed in a positional relationship facing each other in the radial direction with a space therebetween. Similarly, the inner lip portion 282 and the outer lip portion 284 formed on the lower side are formed in a positional relationship facing each other in the radial direction with a space therebetween. Thus, annular grooves 28j are formed between the upper inner lip portion 281 and the outer lip portion 283, and between the lower inner lip portion 282 and the outer lip portion 284, respectively. An annular spring 29 is mounted in the groove 28j. The spring 29 is formed in a U shape in a sectional view of FIG. The spring 29 applies a pressing force radially inward to the inward lip portion 28e, and applies a pressing force radially outward to the outward lip portion 28g. Thereby, the seal surface pressure between the inward lip portion 28e and the outer peripheral surface 55 and the seal surface pressure between the outward lip portion 28g and the groove bottom surface 241 can be improved.

  Next, the tip shape of the outer lip portion 28f will be described. The length in the axial direction of the outer lip portion 28f (the length including a crush margin setting portion 28k described later) is set to a value larger than the length in the axial direction of the inner lip portion 28d. The length is set so as to contact the groove side surfaces 242 and 243. Specifically, a crush margin setting portion 28k that contacts the groove side surfaces 242 and 243 with a crush margin is formed at the tip of the outer lip portion 28f. It can be said that the crushing margin setting portion 28k is formed at a position closer to the outer peripheral surface 28a than the inner peripheral surface 28b of the seal main body 28 at the end of the seal main body 28 in the axial direction. The crush margin setting portion 28k is thinner than the outer lip portion 28f (the portion other than the crush margin setting portion 28k) and the inner lip portion 28d so that it can be easily deformed by contact with the groove side surfaces 242 and 243. Is formed. The upper crush margin setting portion 28k and the lower crush margin setting portion 28k are formed symmetrically with respect to a plane perpendicular to the axial direction. Further, the crushing margin setting portion 28k is formed in a shape that is continuous over the entire circumference in the circumferential direction of the seal body 28, that is, is formed in an annular shape around the axis L2.

  Specifically, the crushing allowance setting unit 28k has a center line L3 (a line passing through the center of the crushing allowance setting unit 28k in the thickness direction) that is a curved line and is formed in a shape protruding in the axial direction, that is, a distorted protruding shape. Is formed. The inner peripheral surface and the outer peripheral surface of the crush margin setting portion 28k are also distorted along the path from the root to the tip of the crush margin setting portion 28k, similarly to the central axis L3. Further, the distortion direction of the crushing margin setting unit 28k is set to the inside in the radial direction. That is, the tip of the crushing margin setting portion 28k before being attached to the seal groove 24 faces the inner side in the radial direction. In other words, the tip of the crushing allowance setting unit 28k is located radially inward from the root of the crushing allowance setting unit 28k.

  Further, the length between both ends in the axial direction of the seal body 28 before the seal member 15 is mounted in the seal groove 24 (that is, the tip of the upper crush margin setting portion 28k and the tip of the lower crush margin setting portion 28k). Is a length from the root to the tip of the crushing margin setting portion 28k so that it is longer than the width in the axial direction of the seal groove 24 (that is, the width between the groove side surfaces 242 and 243). Is set. At this time, a portion of the seal body 28 corresponding to the difference between the length between both ends in the axial direction of the seal body 28 and the width in the axial direction of the seal groove 24 is a crushing margin setting portion 28k. Specifically, the length of the crushing allowance setting portion 28k is set to a value that can absorb the shape error of the seal member 15 due to tolerance and the deformation of the seal member 15 due to thermal expansion. Specifically, for example, if the tolerance, the shape error of the seal member 15 due to thermal expansion, and the assumed deformation amount are 0.5 mm, the total length of the upper and lower two crush margin setting portions 28k is a value of 0.5 mm or more ( For example, it is set to about 1 mm. When the total length of the two upper and lower crushing margin setting sections 28k is about 1 mm, the length of each crushing margin setting section 28k is about 0.5 mm.

  As shown in FIG. 2, in a state where the seal member 15 is mounted in the seal groove 24, one crushing allowance setting portion 28 k contacts (crushes) in a deformed state on the groove side surface 242 on the upper side (pressure chamber 17 side). The other crushing allowance setting portion 28k contacts (contacts with crushing allowance) in a deformed state on the groove side surface 243 on the lower side (cam 14 side). At this time, since the crush margin setting portion 28k is formed in a shape distorted radially inward, the outer peripheral surface of the crush margin setting portion 28k contacts the groove side surfaces 242, 243, and the tip of the crush margin setting portion 28k is Face radially inward. That is, each crushing margin setting portion 28k contacts the groove side surfaces 242 and 243 in a state of being further distorted inward in the radial direction that is the distortion direction.

  Hereinafter, the effect of this embodiment is demonstrated. Since the high-pressure pump 100 includes the seal member 15 provided with the lip portions 28d and 28f on both the inner peripheral surface side, the outer peripheral surface side, and both axial end sides, the pressurizing chamber 17 side from the seal groove 24 is provided. It is possible to effectively suppress the leakage of the medium (fuel, engine oil) between the fuel environment region that is and the oil environment region that is on the internal combustion engine side. In addition, the single seal member 15 can be provided with both a function of suppressing fuel leakage and a function of suppressing engine oil leakage, and a seal member for suppressing fuel leakage and engine oil The number of parts can be reduced as compared with the case where a sealing member for suppression is provided separately.

  Further, since the seal member 15 is formed symmetrically with respect to a plane perpendicular to the axial direction, when assembling the seal member 15 into the seal groove 24, which of the both ends of the seal member 15 is on the pressure chamber 17 side, Assembling can be performed without worrying about the direction of the internal combustion engine, and the assembling property can be improved.

  Further, since the seal member 15 is attached to the seal groove 24 in a state where it is in contact with the groove side surfaces 242 and 243 with a crushing margin, it is possible to prevent the seal member 15 from moving in the seal groove 24 due to the reciprocating movement of the plunger 5. it can. As a result, wear of the inward lip portion 28e that contacts the outer peripheral surface of the plunger 5 and the outward lip portion 28g that contacts the groove bottom surface 241 can be suppressed, and good sealing performance can be secured over a long period of time. In particular, the outward lip portion 28g is not assumed to slide between the groove bottom surface 241 and may have low wear resistance against sliding, but even in this case, the outward lip portion 28 g of wear can be suppressed.

  Further, by actively deforming the crushing margin setting unit 28k, the crushing margin setting unit 28k can absorb a shape error due to tolerance and a shape change due to thermal expansion. Therefore, it can suppress that stress is applied to the both ends of the sealing member 15, and it can suppress that the shape of the sealing member 15 changes with the stress and seal performance falls.

  In the seal member 15, the sealing performance between the outer peripheral surface of the plunger 5 is particularly important. In this respect, since the crushing margin setting portion 28k is formed on the outer side in the radial direction of the seal member 15, the elastic force that the crushing margin setting portion 28k tries to return from the deformed state to the original state is the inner peripheral surface of the seal member 15. Can be suppressed. Therefore, a stable contact state can be ensured between the inner peripheral surface of the seal member 15 and the outer peripheral surface of the plunger 5, and good sealing performance can be exhibited. Further, by forming the crushing allowance setting portion 28k on the outer side in the radial direction, it is possible to prevent the portion on the outer side in the radial direction of the seal member 15 from moving in the axial direction. Wear can be suppressed.

  Further, since the crushing margin is not set and the inner lip portion 28d is provided in a non-contact state on the groove side surfaces 242, 243, the inner lip portion 28d is stable between the inner peripheral surface of the seal member 15 and the outer peripheral surface of the plunger 5. A contact state can be secured. In addition, the space 300 (see FIG. 2) between the upper inner lip portion 28d and the groove side surface 242 is formed with an inlet for the collection passage 25 (see FIG. 1; not shown in FIG. 2). By sufficiently taking a gap between the portion 28d and the groove side surface 242, the space 300 can be enlarged, and the fuel that has flowed into the space 300 can easily flow into the recovery passage 25. Thereby, it can suppress that a fuel leaks to the internal combustion engine side.

  Further, since the crushing margin setting portions 28k are formed at both ends of the seal member 15, the length of each crushing margin setting portion 28k can be shortened compared to the case where it is formed only at one end portion. Since the length can be shortened, it is possible to suppress the crushing allowance setting portion 28k from coming into contact with an unexpected location other than the groove side surfaces 242 and 243 (such as the outer peripheral surface of the plunger 5 and the gap 27 (see FIG. 2)). Thereby, it can suppress that the elastic force of the crushing allowance setting part 28k acts in an unexpected direction, and can suppress the shape change of the seal member 15 by the effect | action to an unexpected direction, and the fall of sealing performance.

  Further, since the crushing margin setting unit 28k is formed in a shape that is distorted inward in the radial direction, the deformation direction of the crushing margin setting unit 28k can be easily controlled. Specifically, the crushing margin setting unit 28k is set inward in the radial direction. Further, the groove side surfaces 242 and 243 can be brought into contact with each other in a distorted deformation state. Accordingly, it is possible to suppress the elastic force of the crush margin setting portion from acting in an unexpected direction due to the crush margin setting portion deforming in an unexpected direction. Moreover, the outer peripheral surface of the crush margin setting portion 28k and the groove bottom surfaces 242, 243 can be brought into contact with each other by setting the crush margin setting portion 28k to a radially inner distorted shape. Thereby, the crushing margin setting portion 28k can easily apply an elastic force to return to the original state, and the elastic force can effectively suppress the movement of the seal member 15 in the axial direction, and deformation due to tolerance and thermal expansion can be prevented. Can absorb effectively. Moreover, it can suppress that the crushing allowance setting part 28k contacts the groove bottom face 241 by making the crushing allowance setting part 28k into the shape distorted to the radial inside. In addition, since the deformation direction of the crushing margin setting unit 28k can be easily controlled, it is possible to suppress the crushing margin setting unit 28k from undergoing creep deformation (destruction) without elastic deformation.

(Second Embodiment)
Next, with reference to FIG. 3, a second embodiment of the present invention will be described with a focus on differences from the above embodiment. The seal body 28 in the seal member 15 of FIG. 3 has a crush allowance setting portion 28k similar to that in the first embodiment formed only on the outer lip portion 283 disposed on the upper (pressurizing chamber side) groove side surface 242 side. The crushing allowance setting portion is not formed on the outer lip portion 284 disposed on the lower (internal combustion engine side) groove side surface 243 side. The tip of the lower outer lip 284 is in contact with the lower groove side surface 243 with no crushing allowance. Further, the length (crushing allowance) of the upper crushing margin setting unit 28k is set to a value that can absorb the shape error due to tolerance and the shape change due to thermal expansion, but the crushing margin setting unit is not set on the lower side. Minutes, for example, a value larger than that of the first embodiment. Except for the tip shapes of the outer lip portions 283 and 284, the second embodiment is the same as the first embodiment. According to this embodiment, in addition to obtaining the same effect as that of the above embodiment, the crushing allowance setting portion is formed only on the upper side, so that the processing cost of the seal member can be suppressed.

(Third embodiment)
Next, with reference to FIG. 4, a third embodiment of the present invention will be described with a focus on differences from the above embodiment. The seal body 28 in the seal member 15 of FIG. 4 has a crush allowance setting portion 28k similar to that of the first embodiment formed only on the outer lip portion 284 disposed on the lower (internal combustion engine side) groove side surface 243 side. The crushing margin setting portion is not formed on the outer lip portion 283 disposed on the groove side surface 242 on the upper side (pressure chamber side). The tip of the upper outer lip 283 is in contact with the upper groove side surface 242 without any crushing allowance. Except for the tip shapes of the outer lip portions 283 and 284, the second embodiment is the same as the first embodiment. 3 and the seal member 15 in FIG. 4 have the same shape, and there is a difference in the mounting direction in the seal groove. According to this embodiment, the same effect as that of the above embodiment can be obtained.

(Fourth embodiment)
Next, with reference to FIG. 5, a fourth embodiment of the present invention will be described with a focus on differences from the above embodiment. In the seal main body 28 of FIG. 5, as in the first embodiment, a crush margin setting portion 28l is formed at the tip of the upper and lower outer lip portions 28f, but the shape of the crush margin setting portion 28l is the same as that of the first embodiment. Is different. Specifically, the crushing margin setting portion 28l is formed in a shape that is distorted in the opposite direction to the distorting direction of the first embodiment, that is, radially outward.

  As shown in FIG. 5, in a state where the seal member 15 is mounted in the seal groove 24, one crushing margin setting portion 28l contacts the upper groove side surface 242 in a deformed state, and the other crushing margin setting portion 28l. Contacts the lower groove side surface 243 in a deformed state. At this time, since the crush margin setting portion 28l is formed in a shape distorted radially outward, the inner peripheral surface of the crush margin setting portion 28l contacts the groove side surfaces 242 and 243, and the tip of the crush margin setting portion 28l. Faces radially outward. That is, each crushing margin setting portion 28l contacts the groove side surfaces 242 and 243 in a state of being further distorted outward in the radial direction that is the distortion direction. Except for the crushing allowance setting unit 28l, the second embodiment is the same as the first embodiment.

  According to the present embodiment, in addition to obtaining the same effect as the above-described embodiment, the crush margin setting portion 28l has a shape that is distorted outward in the radial direction. It can suppress contacting with an outer peripheral surface. Further, it is possible to suppress the lower crushing margin setting portion 28l from being disposed in the gap 27. Furthermore, it is possible to prevent the entrance of the collection passage 25 (see FIG. 1) formed in the space 300 from being blocked by the crushing allowance setting unit 28l.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described with reference to FIG. In the seal body 28 of FIG. 6, a crush margin setting portion 281 similar to that of the fourth embodiment is formed only on the upper outer lip portion 283, and a crush margin setting portion is formed on the lower outer lip portion 284. Not. The tip of the lower outer lip 284 is in contact with the lower groove side surface 243 with no crushing allowance. Except for the tip shapes of the outer lip portions 283 and 284, the second embodiment is the same as the first embodiment. According to this embodiment, the same effect as that of the above embodiment can be obtained.

(Sixth embodiment)
Next, with reference to FIG. 7, a sixth embodiment of the present invention will be described focusing on the differences from the above embodiment. In the seal body 28 of FIG. 7, a crush margin setting portion 28l similar to that of the fourth embodiment is formed only in the lower outer lip portion 284, and a crush margin setting portion is formed in the upper outer lip portion 283. Not. The tip of the upper outer lip 283 is in contact with the upper groove side surface 242 without any crushing allowance. Except for the tip shapes of the outer lip portions 283 and 284, the second embodiment is the same as the first embodiment. The shape of the seal member of FIG. 6 and that of FIG. 7 are the same, and there is a difference in the mounting direction in the seal groove. According to this embodiment, the same effect as that of the above embodiment can be obtained.

(Seventh embodiment)
Next, with reference to FIG. 8, a seventh embodiment of the present invention will be described focusing on the differences from the above embodiment. In the seal main body 28 of FIG. 8, as in the first embodiment, a crush margin setting portion 28m is formed at the tip of the upper and lower outer lip portions 28f. The shape of the crush margin setting portion 28m is the same as that of the first embodiment. Is different. Specifically, the crushing margin setting unit 28m is not formed in a distorted shape, but is formed in a shape in which the center line L4 is a straight line. In FIG. 8, the direction of the crushing margin setting portion 28 m (the direction of the center line L <b> 4) is a direction parallel to the axial direction of the seal member 15. In other words, the direction of the crushing margin setting portion 28m is perpendicular to the groove side surfaces 242 and 243. In FIG. 8, the crushing margin setting unit 28m before deformation is shown for easy understanding. However, the crushing margin setting unit 28m actually contacts the groove side surfaces 242 and 243 in a deformed state. . At this time, the crushing margin setting unit 28m may contact in a state of being distorted inward in the radial direction, or may be in contact in a state of being distorted outward in the radial direction. Except for the crushing allowance setting unit 28m, the second embodiment is the same as the first embodiment. According to this embodiment, the same effect as that of the above embodiment can be obtained.

(Eighth embodiment)
Next, with reference to FIG. 9, an eighth embodiment of the present invention will be described focusing on the differences from the above embodiment. 9 has a crush margin setting portion 28m similar to that of the seventh embodiment formed only on the upper outer lip portion 283, and a crush margin setting portion formed on the lower outer lip portion 284. Not. The tip of the lower outer lip 284 is in contact with the lower groove side surface 243 with no crushing allowance. Except for the tip shapes of the outer lip portions 283 and 284, the second embodiment is the same as the first embodiment. According to this embodiment, the same effect as that of the above embodiment can be obtained.

(Ninth embodiment)
Next, with reference to FIG. 10, a ninth embodiment of the present invention will be described with a focus on differences from the above embodiment. 10 has a crush margin setting portion 28m similar to that of the fourth embodiment formed only in the lower outer lip portion 284, and a crush margin setting portion is formed in the upper outer lip portion 283. Not. The tip of the upper outer lip 283 is in contact with the upper groove side surface 242 without any crushing allowance. Except for the tip shapes of the outer lip portions 283 and 284, the second embodiment is the same as the first embodiment. The shape of the seal member in FIG. 9 and the shape of the seal member in FIG. 10 are the same, and the mounting direction in the seal groove is different. According to this embodiment, the same effect as that of the above embodiment can be obtained.

(Other embodiments)
In addition, this invention is not limited to the said embodiment, A various change is possible to the limit which does not deviate from description of a claim. For example, in FIGS. 2, 5, and 8, the upper and lower crushing allowance setting units have the same distortion direction (in the case of FIGS. 2 and 5) or straight lines (in the case of FIG. 8). Alternatively, it may be linear. Specifically, on the upper side, a crushed allowance setting part of one of a shape distorted radially inward, a shape distorted radially outward, or a straight line is formed, and an upper crushed allowance setting is formed on the lower side. You may form the distortion direction or linear crushing margin setting part different from a part.

  Further, in the above embodiment, the example has been described in which the crushing margin setting unit is formed in a shape that is continuous over the entire circumference in the circumferential direction, but the crushing margin setting unit that is divided into a plurality at intervals in the circumferential direction. It may be formed. Moreover, the sealing member of the present invention may be applied to a high-pressure pump other than the common rail system, or the present invention may be applied to an apparatus other than the high-pressure pump. In the above embodiment, the example in which the seal groove is formed by the combination of the cylinder 3 and the cover member 26 (see FIG. 2) has been described. However, the seal groove may be formed only by the cylinder, or only by the cover member. A seal groove may be formed.

  In the above embodiment, an example in which the inward lip portion 28e and the outward lip portion 28g are formed at two locations on both ends in the axial direction has been described. However, the lip portion is formed at several locations in the axial direction. It is also good.

  8 to 10, the example in which the crushing margin setting portion 28m is formed in a direction perpendicular to the groove side surfaces 242 and 243 has been described. However, the linear shape is inclined in the direction inclined with respect to the groove side surfaces 242 and 243. A crushing allowance setting unit may be formed. Specifically, for example, a linear crush margin setting portion inclined radially inward may be formed, or a linear crush margin setting portion inclined radially outward may be formed. According to this, it is possible to easily control the deformation direction of the crushing margin setting unit.

5 Plunger (shaft member)
55 Plunger outer peripheral surface (shaft outer peripheral surface)
15 Seal member 24 Seal groove 241 Bottom surface of seal groove (bottom surface of groove)
242 and 243 Side surface of seal groove (side surface of groove)
28 Seal body 28a Outer peripheral surface of the seal body (Outer seal surface)
28b Inner peripheral surface of the seal body (seal inner peripheral surface)
28k, 28l, 28m squashing allowance setting part

Claims (12)

A seal member (15) provided in an annular seal groove (24) formed at a position facing the shaft outer peripheral surface which is the outer peripheral surface (55) of the shaft member (5) reciprocating in the axial direction,
An inner peripheral surface (28b) that contacts the outer peripheral surface of the shaft so as to suppress leakage of the medium from one side of the axial direction to the other side of the seal groove, and the seal groove that faces the outer peripheral surface of the shaft An annular seal body (28) having an outer peripheral surface (28a) in contact with the groove bottom surface (241) which is the surface of
A surface facing the axial direction of the seal groove as a groove side surface (242, 243)
The seal body is a seal member having a crush margin setting portion (28k, 28l, 28m) that contacts a side surface of the groove with a crush margin at a position radially outside at least one of both ends in the axial direction.   The seal member according to claim 1, wherein the crush margin setting portion is formed at both ends of the seal body in the axial direction.   The seal member according to claim 1, wherein the crush margin setting portion is formed only at one end in the axial direction of the seal body.   The seal member according to any one of claims 1 to 3, wherein the crush margin setting portion (28k, 28l) is formed in a distorted projection shape.   The seal member according to any one of claims 1 to 4, wherein the crush margin setting portion (28k) is formed in a protruding shape whose tip is directed radially inward.   The seal member according to any one of claims 1 to 4, wherein the crush margin setting portion (281) is formed in a protruding shape whose tip is directed in a radially outward direction. The seal body is
A plurality of inward lip portions (28e) that are formed at intervals in the axial direction on the inner peripheral surface of the seal that is the inner peripheral surface of the seal body, and that are in contact with the outer peripheral surface of the shaft;
The seal inner peripheral surface between the plurality of inward lip portions, and an inner concave surface (28h) that forms a gap with the shaft outer peripheral surface. The sealing member as described. The seal body is
A plurality of outwardly facing lip portions (28g) that are formed at intervals in the axial direction on the seal outer peripheral surface that is the outer peripheral surface of the seal body, and that are in contact with the groove bottom surface;
The seal member according to claim 7, which has an outer concave surface (28 i) that forms a gap between the outer peripheral surface of the seal between the plurality of outward lip portions and the bottom surface of the groove. The seal body is
An intermediate portion (28c) in which no lip portion is formed on the inner peripheral surface and the outer peripheral surface;
An annular inner lip portion (28d) provided so as to protrude in the axial direction from the radially inner side at the axial end portion of the intermediate portion, and the inward lip portion formed on the inner peripheral surface;
An annular outer lip portion (28f) provided so as to protrude in the axial direction from the radially outer side at the axial end portion of the intermediate portion and having the outward lip portion formed on the outer peripheral surface;
The crushing allowance setting part is formed at the tip of the outer lip part,
The seal member according to claim 8, wherein the inner lip portion is provided on the side surface of the groove in a non-contact state.   A spring (29) for applying a pressing force to the inward lip portion and the outward lip portion in a groove (28j) formed between the inner lip portion and the outer lip portion of the seal body. Item 10. The sealing member according to Item 9.   The seal member includes a plunger (5) as the shaft member, and a cylinder (3) that accommodates the plunger so as to be reciprocally movable and slidable. The pressurizing chamber (17) formed between the wall surfaces pressurizes the liquid, and is used for the high-pressure pump (100) that discharges the liquid after pressurization. Seal member. A plunger (5);
A cylinder (3) in which the plunger is reciprocally movable in an axial direction and slidably received, and an annular seal groove (24) is formed at a position facing the outer peripheral surface (55) of the plunger;
A suction valve portion (1) for opening and closing a liquid suction port to a pressurizing chamber (17) formed between an end surface (53) of the plunger and an inner wall surface of the cylinder;
A discharge valve (4) provided in a discharge passage (23) for discharging the liquid pressurized in the pressurizing chamber and opening and closing the discharge passage;
The seal member (15) according to any one of claims 1 to 10, provided in the seal groove,
A high pressure pump (100) comprising:

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