JP6670720B2 - High pressure fuel supply pump - Google Patents

Description

  The present invention relates to a high-pressure fuel supply pump, and more particularly to a high-pressure fuel supply pump having a function of avoiding cavitation erosion generated near a relief seat portion of a housing portion where the relief valve contacts the relief valve.

  Patent Literature 1 employs the same structure as the relief valve studied by this patent, and has a relief valve, a relief valve holder for holding the relief valve, and a direction opposite to the relief valve holder, and the relief valve is closed. When the relief valve is opened, a recess is provided in the housing opposite to the relief valve to reduce the speed of the fuel flowing through the relief valve when the relief valve is opened. Due to the recess, the flow path surface area of the housing increases, so that the speed of the fuel flowing through the relief valve decreases, and the occurrence of cavitation can be suppressed.

JP 2010-169083 A

  The prior arts have the following problems.

  The high-pressure fuel supply pump studied in this patent has a structure in which a flow path having a relief valve and a pressurizing chamber are communicated with each other. In a fuel suction process, when the plunger in the pressurizing chamber is lowered, the relief valve is turned off. It is in a closed state in contact with the housing.

  Since the plunger is lowered in a state where the relief valve is closed, the fuel existing in the relief valve flow path is pulled toward the pressurizing chamber, and the density and pressure of the fuel rapidly decrease due to the compressive effect of the liquid.

  The relief seat portion is a position where the relief valve and the housing are in contact with each other. In the vicinity of the relief seat, a narrow gap flow path is formed by the relief valve and the housing.

  When the plunger is lowered, the fuel is pulled toward the pressurizing chamber, so that a turbulent vortex is generated in the narrow gap flow path, the flow speed is increased, and the pressure is reduced.

  That is, there is a problem that cavitation occurs due to the decrease in density and pressure and impact energy is generated due to collapse of cavitation bubbles, thereby damaging the housing wall near the relief sheet portion.

  Damage due to cavitation erosion near the relief seat portion described above causes a leakage flow problem in which the high-pressure fuel returns from the relief seat portion of the relief valve to the pressurized chamber when the relief valve is closed. .

  Therefore, an object of the present invention is to suppress cavitation erosion in the relief seat portion and suppress the above-described problem of fuel leakage flow.

In order to solve the above-described problems, in the present invention, a pressurized chamber whose volume is changed by a reciprocating operation of a plunger, a suction passage for sucking fuel into the pressurized chamber, and a fuel pressurized in the pressurized chamber are provided. A discharge passage for discharging, a high-pressure fuel supply pump including a relief valve that opens when the fuel in the discharge passage exceeds a set value and returns the fuel in the discharge passage to the pressurized chamber; A relief valve holder for holding, and a relief spring for urging the relief valve in the valve closing direction by urging the relief valve holder, the relief valve holder, or a housing portion facing the relief valve holder the portion recessed in a direction in which the flow passage is widened between the relief valve holder and the housing portion is formed, the relief valve holder the housing in a direction crossing the axial direction of the relief valve Has an outer peripheral portion forming a passage between said recess portion is formed in the relief valve holder along the axial direction of the relief valve to the wall on the opposite side to the passage.

  ADVANTAGE OF THE INVENTION According to this invention comprised as mentioned above, the position which cavitation produces | generates remarkably can be moved from the clearance flow path of a relief sheet part to a recessed part, and the cavitation in a relief sheet part, and the occurrence of erosion damage Can be suppressed.

FIG. 1 is a diagram illustrating an overall configuration of a system according to a first exemplary embodiment of the present invention. FIG. 2 is a diagram illustrating a cross section of the relief mechanism according to the first embodiment of the present invention. FIG. 6 is a diagram illustrating a state in which the vicinity of a relief sheet unit 205 is enlarged. FIG. 8 is an enlarged view of a relief valve mechanism 200 according to a second embodiment of the present invention. FIG. 10 is an enlarged view of a relief valve mechanism 200 according to a third embodiment of the present invention. FIG. 10 is an enlarged view of a relief valve mechanism 200 according to a fourth embodiment of the present invention. FIG. 11 is an enlarged view of a relief valve mechanism 200 according to a fifth embodiment of the present invention. FIG. 11 is an enlarged view of a relief valve mechanism 200 according to a sixth embodiment of the present invention. FIG. 13 is an enlarged view of a relief valve mechanism 200 according to a seventh embodiment of the present invention. FIG. 14 is an enlarged view of a relief valve mechanism 200 according to an eighth embodiment of the present invention. FIG. 19 shows an enlarged view of a relief valve mechanism 200 according to Embodiment 9 of the present invention. FIG. 14 shows an enlarged view of a relief valve mechanism 200 according to Embodiment 10 of the present invention. FIG. 21 shows an enlarged view of a relief valve mechanism 200 according to Embodiment 11 of the present invention. FIG. 16 is an enlarged view of a relief valve mechanism 200 according to Embodiment 12 of the present invention. FIG. 19 is an enlarged view of a relief valve mechanism 200 according to Embodiment 13 of the present invention. FIG. 16 is an enlarged view of a relief valve mechanism 200 different from FIG. 15 of Embodiment 13 of the present invention. FIG. 17 is an enlarged view of a relief valve mechanism 200 different from FIGS. 15 and 16 of the thirteenth embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 shows the overall configuration of a system for implementing the present invention. The portion enclosed by a broken line in FIG. 1 shows a pump housing 1 of the high-pressure fuel supply pump, and the mechanism and components shown in the broken line are integrally incorporated therein.

  The fuel in the fuel tank 20 is pumped up by the feed pump 21 and sent to the fuel inlet 10 a of the pump housing 1 through the suction pipe 28. The fuel that has passed through the fuel suction port 10a reaches the suction port 30a of the electromagnetic suction valve mechanism 30, which constitutes a variable capacity mechanism, via the first suction passage 10b, the pressure pulsation reduction mechanism 9, and the second suction passage 10c. The first suction passage 10b is a passage connecting the fuel suction port 10a and the pressure pulsation reducing mechanism 9, and the second suction passage 103 is a passage connecting the pressure pulsation reducing mechanism 9 and the electromagnetic suction valve mechanism 30.

  The electromagnetic suction valve mechanism 30 includes an electromagnetic coil 30b. When the electromagnetic coil 30b is energized, the electromagnetic plunger 30c compresses the spring 33 and moves to the right in FIG. Will be maintained. At this time, the suction valve body 31 attached to the tip of the electromagnetic plunger 30c opens the suction port 32 communicating with the pressurizing chamber 11 of the high-pressure fuel supply pump. When the electromagnetic coil 30 b is not energized and there is no fluid pressure difference between the second suction passage 10 c (suction port 30 a) and the pressurizing chamber 11, the suction valve body is biased by the spring 33. 31 is urged in the valve closing direction (leftward in FIG. 1), and the suction port 32 is closed, and this state is maintained.

  When the plunger 2 is displaced downward in FIG. 1 by the rotation of the cam of the internal combustion engine, which will be described later, and is in the suction process state, the volume of the pressurizing chamber 11 increases, and the fuel pressure therein decreases. In this step, when the fuel pressure in the pressurizing chamber 11 becomes lower than the pressure in the second suction passage 10c (the suction port 30a), the suction valve 31 is forced to open by the fluid pressure difference of the fuel (the suction valve 31). Is generated in the right direction in FIG. 1). With this valve opening force, the suction valve body 31 opens the valve by overcoming the urging force of the spring 33 and opens the suction port 32. In this state, when a control signal from the ECU 27 is applied to the electromagnetic suction valve mechanism 30, a current flows through the electromagnetic coil 30b of the electromagnetic suction valve 30, and the electromagnetic plunger 30c further compresses the spring 33 by the magnetic urging force. It moves to the right in FIG. 1 to maintain the state where the suction port 32 is open.

  When the plunger 2 shifts from the suction process to the compression process (the ascending process from the lower starting point to the upper starting point) with the input voltage applied to the electromagnetic suction valve mechanism 30 maintained, the energized state of the electromagnetic coil 30b is changed. Since it is maintained, the magnetic urging force is maintained, and the suction valve body 31 still maintains the open state. Although the volume of the pressurizing chamber 11 decreases with the compression movement of the plunger 2, in this state, the fuel once sucked into the pressurizing chamber 11 returns to the suction valve body 31 and the suction port 32 in the valve-open state again. And the pressure is returned to the second suction passage 10c (suction port 30a), so that the pressure in the pressurizing chamber 11 does not increase. This step is called a return step.

  In the return step, when the energization of the electromagnetic coil 30b is stopped, the magnetic biasing force acting on the electromagnetic plunger 30c is erased after a certain time (after a magnetic or mechanical delay time). Then, the suction valve body 31 is moved leftward in FIG. 1 by the urging force of the spring 33 constantly acting on the suction valve body 31 to close the suction port 32. When the suction port 32 is closed, the fuel pressure in the pressurizing chamber 11 increases with the rise of the plunger 2 from this time. Then, when the fuel pressure in the pressurizing chamber 11 exceeds a pressure larger than the fuel pressure of the discharge port 13 by a predetermined value, the fuel remaining in the pressurizing chamber 11 passes through the discharge valve mechanism 8, The high-pressure discharge is performed and supplied to the common rail 23. This step is called an ejection step. As described above, the compression step of the plunger 2 includes the return step and the discharge step.

  During the return process, pressure pulsation is generated in the second suction passage by the fuel returned to the second suction passage 10c, but this pressure pulsation only slightly flows back from the suction port 10a to the suction pipe 28, Most of the return of the fuel is absorbed by the pressure pulsation reduction mechanism 9. By controlling the timing at which the electromagnetic coil 30c of the electromagnetic suction valve mechanism 30 is de-energized, the amount of high-pressure fuel discharged can be controlled. If the timing of releasing the power supply to the electromagnetic coil 30b is advanced, the ratio of the return process in the compression process is reduced, and the ratio of the discharge process is increased.

  That is, the amount of fuel returned to the second suction passage 10c (the suction port 30a) is reduced, and the amount of fuel discharged at high pressure is increased. On the other hand, if the timing of the above-described energization release is delayed, the ratio of the return process in the compression process is increased and the ratio of the discharge process is reduced. That is, more fuel is returned to the second suction passage 10c, and less fuel is discharged at high pressure. The timing of the above-described de-energization is controlled by a command from the ECU. As described above, the amount of fuel discharged at a high pressure can be set to an amount required by the internal combustion engine by controlling the timing at which the energization of the electromagnetic coil is released by the ECU.

  In the pump housing 1, a discharge valve mechanism 8 is provided on the outlet side of the pressurizing chamber 11 between the discharge port (discharge-side pipe connection part) 13. The discharge valve mechanism 8 includes a seat member 8a, a discharge valve 8b, a discharge valve spring 8c, and a holding member (discharge valve stopper) 8d. When there is no fuel pressure difference between the pressurizing chamber 11 and the discharge port 13, the discharge valve 8b is pressed against the seat member 8a by the urging force of the discharge valve spring 8c and is in a closed state. When the fuel pressure in the pressurizing chamber 11 exceeds a pressure higher than the fuel pressure in the discharge port 13 by a predetermined value, the discharge valve 8b opens against the discharge valve spring 8c, and Is discharged to the common rail 23 through the discharge port 13.

  After the discharge valve 8b is opened and comes into contact with the holding member 8d, the operation is restricted. Therefore, the stroke of the discharge valve 8b is appropriately determined by the holding member 8d. If the stroke is too large, the fuel discharged to the fuel discharge port 13 flows back into the pressurizing chamber 11 again due to the delay in closing of the discharge valve 8b, so that the efficiency of the high-pressure pump is reduced. . Also, when the discharge valve 8b repeats the valve opening and closing movements, the holding member 8d guides the discharge valve to move only in the stroke direction. With the above configuration, the discharge valve mechanism 8 is a check valve that restricts the flow direction of the fuel.

  The required amount of the fuel guided to the fuel inlet 10 a is pressurized to a high pressure by the reciprocating motion of the plunger 2 in the pressurizing chamber 11 of the pump body 1. To the common rail 23 which is a high pressure pipe. An injector 24 and a pressure sensor 26 are mounted on the common rail 23. The injectors 24 are mounted in accordance with the number of cylinders of the internal combustion engine, and operate the opening / closing valves according to control signals from the ECU 27 to inject fuel into the cylinders.

Next, a description will be given of a fuel relief operation in the first embodiment when an abnormally high pressure is generated in a high-pressure portion such as the common rail 23 due to a failure of the injector 24 or the like. The pump housing 1 is provided with a relief passage 300 that connects the discharge passage 12 and the pressurizing chamber 11, and restricts the flow of fuel in the relief passage 300 to only one direction from the discharge passage 12 to the pressurizing chamber 11. A relief valve mechanism 200 is provided. In the following embodiment, the abnormally high-pressure fuel in the discharge passage 12 can be returned to the pressurizing chamber 11 by the relief valve mechanism 200. However, the present invention is not limited to the pressurizing chamber 11, and is not limited to the low-pressure side. For example,
Further, as shown in FIG. 1, the fuel passing through the relief passage 300 flows from the discharge passage 12 to the pressurizing chamber 11. That is, the structure is such that the relief valve mechanism 200 and the pressurizing chamber communicate with each other.

  FIG. 2 shows a cross section of the relief valve mechanism according to the first embodiment of the present invention. The relief valve mechanism 200 includes a relief valve 201, a relief valve holder 202 that holds the relief valve 201, a relief spring 203 that biases the relief valve, and a housing 204 that engages with the relief valve to seal fuel. The position where the relief valve 201 and the housing 204 contact each other is called a relief seat portion 205.

  The high-pressure fuel supply pump according to the present embodiment has a structure in which the pressurizing chamber 11 and the relief valve passage are communicated with each other. In a suction process in which fuel flows into the pressurizing chamber 11, the plunger 2 inside the pressurizing chamber 11 is used. When the pressure is lowered, the relief valve 201 comes into contact with the housing 204 and the relief seat portion 205 to be in a closed state.

  Since the relief valve 201 is closed, when the plunger 2 is lowered, the fuel in the relief valve passage is pulled toward the pressurizing chamber 11. At this time, the density and pressure in the relief valve passage decrease due to the compressive effect of the liquid.

  FIG. 3 shows a state in which the vicinity of the relief sheet unit 205 is enlarged. Near the relief seat 205, a narrow gap flow path 207 sandwiched between the relief valve 201 and the housing 204 is formed. Here, when the plunger 2 is lowered in a state where the relief valve 201 is closed, the fuel is pulled toward the pressurizing chamber 11, so that a turbulent vortex is generated in the gap flow path 207. Due to the generation of the turbulent vortex, the flow speed is increased and the pressure is reduced.

  As a result, the pressure in the narrow gap flow path 207 decreases due to the decrease in the density and the speed of the flow described above, and cavitation occurs. In addition, the collapse of the generated cavitation bubbles generates high impact energy, and the wall surface of the housing 204 near the relief sheet portion 205 is damaged by erosion. This damage causes a problem that the damaged area and fuel leak when the relief valve 201 is closed.

  Therefore, as shown in FIG. 2, a recess 206 is provided in a direction in which a flow path formed between the relief valve holder and the housing expands with respect to the housing 204 located at a position opposed to the relief valve holder 202.

  As described above, the high-pressure fuel supply pump according to the present embodiment includes the pressurizing chamber 1 whose volume changes due to the reciprocating operation of the plunger 2, the suction passages (10b, 10c) for sucking fuel into the pressurizing chamber 1, A discharge passage 12 for discharging fuel pressurized in the chamber 11, and a relief valve 201 that opens when the fuel in the discharge passage 12 exceeds a set value and returns the fuel in the discharge passage 12 to the pressurized chamber 11. ing. Further, the high-pressure fuel supply pump includes a relief valve holder 202 that holds the relief valve 201, and a relief spring 203 that urges the relief valve 201 in the valve closing direction by urging the relief valve holder 202. The relief valve holder 202 or the relief valve holder is located in a direction opposite to the relief valve holder 202 and in the relief valve passage 300 formed by the housing 204 in contact with the relief valve 201 when the relief valve 201 is closed. A recess 206 is formed in a housing 204 facing the housing 202 in a direction in which a flow path between the relief valve holder 202 and the housing 204 expands.

  Due to the recess 206, the turbulent vortex generated in the narrow gap flow path moves to the recess. That is, since the position where cavitation occurs can be changed from the narrow gap flow channel to the concave portion, cavitation generation around the relief sheet portion and erosion damage due to it can be suppressed.

  FIG. 4 is an enlarged view of the relief valve mechanism 200 according to the second embodiment of the present invention. With respect to the relief valve holder 202 holding the relief valve 201, a recess 206 is provided at a position opposed to the housing 204 in a direction in which a flow path formed between the relief valve holder and the housing spreads. That is, in the high-pressure fuel supply pump of this embodiment, the relief valve holder 202 has an outer peripheral portion that forms a flow path between the relief valve holder 202 and the housing 204 when the relief valve 201 is opened. The recess 206 is formed on the outer periphery of the relief valve holder 202. As shown in FIG. 4, the relief valve holder 202 has an outer peripheral portion that forms a flow path between the relief valve 201 and the housing 204 in a direction intersecting with the axial direction of the relief valve 201. The portion is formed in a direction along the axial direction of the relief valve 201.

  More specifically, the recess 206 is formed in a part of the outer peripheral portion of the relief valve holder 202 on the inner diameter side as shown in FIG. 4 in a direction along the axial direction of the relief valve 201 (vertical direction in FIG. 4). . Specifically, the recess 206 is formed so as to be recessed from the upstream side to the downstream side of the relief valve 201 at a part on the inner diameter side of the outer peripheral portion of the relief valve holder 202 as shown in FIG.

  For the same reason as the mechanism described in the first embodiment, the position where cavitation occurs can be moved from the relief sheet portion to the concave portion, so that erosion damage in the relief sheet portion can be suppressed.

  FIG. 5 is an enlarged view of the relief valve mechanism 200 according to the third embodiment of the present invention. With respect to the relief valve holder 202 that holds the relief valve 201, a recess 206 is formed in a direction that intersects with the axial direction in which the relief valve 201 moves or a direction that intersects at right angles with a side surface located at the outermost periphery of the relief valve holder 202. Is installed.

  That is, in the high-pressure fuel supply pump according to the present embodiment, the relief valve holder 202 has an outer peripheral portion that forms a passage between the relief valve 201 and the housing 204 in a direction along the axial direction of the relief valve 201, and the concave portion 206 The relief valve 201 is formed on the outer periphery of the valve holder 202 in a direction intersecting the axial direction of the relief valve 201.

  For the same reason as the mechanism described in the first embodiment, the position where cavitation occurs can be moved from the relief sheet portion to the concave portion, so that erosion damage in the relief sheet portion can be suppressed.

  FIG. 6 is an enlarged view of a relief valve mechanism 200 according to Embodiment 4 of the present invention. With respect to the relief valve holder 202 that holds the relief valve 201, a surface opposite to the surface of the relief valve holder 202 that faces the housing 204, and is recessed in a direction along the axial direction in which the relief valve 201 moves. A unit 206 is provided.

  That is, in the high-pressure fuel supply pump of the present embodiment, the relief valve holder 202 has an outer peripheral portion that forms a passage between the relief valve 201 and the housing 204 in a direction intersecting the axial direction of the relief valve 201 (the left-right direction in FIG. 6). A recess 206 is formed on the wall surface of the relief valve holder 202 opposite to the above-mentioned passage so as to extend along the axial direction of the relief valve 201.

  For the same reason as the mechanism described in the first embodiment, the position where cavitation occurs can be moved from the relief sheet portion to the concave portion, so that erosion damage in the relief sheet portion can be suppressed.

  FIG. 7 is an enlarged view of a relief valve mechanism 200 according to Embodiment 5 of the present invention. With respect to the relief valve holder 202 holding the relief valve 201, a direction intersecting with the axial direction in which the relief valve moves, with respect to a side surface located on the inner diameter side than a side surface located at the outermost diameter of the relief valve holder 202, or A recess 206 is provided in a direction orthogonal to the direction. For the same reason as the mechanism described in the first embodiment, the position where cavitation occurs can be moved from the relief sheet portion to the concave portion, so that erosion damage in the relief sheet portion can be suppressed.

  FIG. 8 is an enlarged view of a relief valve mechanism 200 according to Embodiment 6 of the present invention. With respect to the relief valve holder 202 holding the relief valve 201, a surface opposite to the surface of the relief valve holder 202 opposing the housing 204. A recess 206 is provided in a direction along an axial direction in which the relief valve moves with respect to a surface located farthest away. For the same reason as the mechanism described in the first embodiment, the position where cavitation occurs can be shifted from the relief sheet portion to the concave portion, so that erosion damage at the relief sheet portion can be suppressed.

  FIG. 9 is an enlarged view of a relief valve mechanism 200 according to Embodiment 7 of the present invention. A flow path is formed between the relief valve holder 202 and the housing 204 in the same direction as the axial direction in which the relief valve 201 moves. A recess 206 is provided on the surface of the housing 204 forming the flow path in a direction intersecting with the axial direction in which the relief valve 201 moves or in a direction orthogonal to the axial direction.

  That is, in the high-pressure fuel supply pump of the present embodiment, the housing 204 forms a passage between the relief valve holder 202 and the relief valve 201 when the relief valve 201 is opened, and is located on the outer diameter side with respect to this passage. In the passage formed in the same direction as the axial direction in which the valve moves, the recess 206 is formed on the side surface of the housing 204 in a direction intersecting with or perpendicular to the axial direction in which the relief valve 201 moves.

  For the same reason as the mechanism described in the first embodiment, the position where cavitation occurs can be moved from the relief sheet portion to the concave portion, so that erosion damage in the relief sheet portion can be suppressed.

  FIG. 10 is an enlarged view of a relief valve mechanism 200 according to Embodiment 8 of the present invention. The cross-sectional shape in the axial direction of the relief valve 201 of the recess described in the first to seventh embodiments is rectangular. The cross-sectional shape of the recess in the axial direction of the relief valve 201 is not limited to a rectangle, but may be a triangle as shown in FIG. In terms of ease of manufacture, a triangular shape is easier than a rectangular shape.

  FIG. 11 is an enlarged view of a relief valve mechanism 200 according to Embodiment 9 of the present invention. The cross-sectional shape of the recess described in the first to eighth embodiments is rectangular or triangular. FIG. 11 shows that the cross-sectional shape in the axial direction of the relief valve is formed in a streamlined manner. However, the shape does not need to be specially specified, that is, the cross-sectional shape may be any shape.

  FIG. 12 is an enlarged view of a relief valve mechanism 200 according to Embodiment 10 of the present invention. As shown in FIG. 12, the recesses described in the first to ninth embodiments are dug in the circumferential direction in the shape of an annular ring 208. That is, as shown in FIG. 12, the concave portion 206 is dug into a ring in a circumferentially symmetrical shape.

  FIG. 13 is an enlarged view of a relief valve mechanism 200 according to Embodiment 11 of the present invention. As shown in FIG. 13, the recessed portions described in the first to ninth embodiments are not formed by connected flow paths in an axially symmetrical annular direction. Are scattered around.

  FIG. 14 is an enlarged view of a relief valve mechanism 200 according to Embodiment 12 of the present invention. As shown in FIG. 14, the recessed portions described in the first to ninth embodiments are not formed by continuous flow paths in an axially symmetric annular direction. Scattered in state.

  15, 16, and 17 are enlarged views of a relief valve mechanism 200 according to Embodiment 13 of the present invention. The recessed portions described in the first to ninth embodiments can be applied to the relief valve holder and the housing having the shapes illustrated in FIGS. 15, 16, and 17, and have the same effects as the structures described in the first to ninth embodiments. Can be put out.

DESCRIPTION OF SYMBOLS 1 ... Pump housing, 2 ... Plunger, 8 ... Discharge valve mechanism, 9 ... Pressure pulsation reduction mechanism, 10b ... Second suction passage, 10c ... Second suction passage, 11 ... Pressurizing chamber, 12 ... Discharge passage, 20 ... Fuel Tank, 23 ... common rail, 24 ... injector, 26 ... pressure sensor, 30 ... electromagnetic suction valve mechanism, 200 ... relief valve mechanism, 201 ... relief valve, 202 ... relief valve holder, 203 ... relief spring, 204 ... housing, 205 ... relief Sheet, 206 recessed part ..., 207 ... gap passage, 208 ... annular ring, 209 ... plural grooves, 300 ... relief passage

Claims (10)

A pressurizing chamber whose volume changes due to the reciprocating movement of the plunger;
A suction passage for sucking fuel into the pressurizing chamber,
A discharge passage for discharging the fuel pressurized in the pressurizing chamber,
In a high-pressure fuel supply pump including a relief valve that opens when the fuel in the discharge passage exceeds a set value and returns the fuel in the discharge passage to the pressurized chamber,
A relief valve holder for holding the relief valve,
A relief spring for urging the relief valve in the valve closing direction by urging the relief valve holder,
The relief valve holder, or a recess portion is formed in a direction in which a flow path between the relief valve holder and the housing portion spreads in a housing portion facing the relief valve holder ,
The relief valve holder has an outer peripheral portion that forms a passage between the relief valve holder and the housing in a direction intersecting with an axial direction of the relief valve,
A high-pressure fuel supply pump in which the recess is formed on a wall surface of the relief valve holder opposite to the passage so as to extend along an axial direction of the relief valve . The high-pressure fuel supply pump according to claim 1,
Before SL is recessed portion, the high-pressure fuel supply pump formed in the outer peripheral portion of the relief valve holder. The high-pressure fuel supply pump according to claim 1,
Before SL is recessed portion, the high-pressure fuel supply pump which is formed in a direction along the axial direction of the relief valve to the outer peripheral portion of the relief valve holder. The high-pressure fuel supply pump according to claim 3,
The high-pressure fuel supply pump, wherein the concave portion is formed in a part of the relief valve holder on the inner diameter side of the outer peripheral portion in a direction along the axial direction of the relief valve. The high-pressure fuel supply pump according to claim 1,
Before SL recessed portion, the high-pressure fuel supply pump which is formed in a direction crossing the axial direction of the relief valve to the outer peripheral portion of the relief valve holder. In the high-pressure fuel supply pump having the recessed portion according to claims 1 to 5,
A high-pressure fuel supply pump formed such that a cross-sectional shape of the recess in the axial direction of the relief valve is triangular. In the high-pressure fuel supply pump having the recessed portion according to claims 1 to 5,
The high-pressure fuel supply pump, wherein the recess is formed in an arbitrary shape such that a cross-sectional shape in the axial direction of the relief valve is represented by a streamline. In the high-pressure fuel supply pump having the recessed portion according to claims 1 7,
The high-pressure fuel supply pump is characterized in that the concave portion is formed in an annular shape with a circumferentially symmetrical shape in the circumferential direction. In the high-pressure fuel supply pump having the recessed portion according to claims 1 8,
A high-pressure fuel supply pump, wherein a plurality of grooves formed by the recesses are dug in an axially symmetric annular direction. In the high-pressure fuel supply pump having the recessed portion according to claims 1 7,
A high-pressure fuel supply pump, wherein a plurality of grooves formed by the recesses are dug at random.

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