DE112019002218T5 - Fuel supply pump - Google Patents

Abstract

A fuel supply pump is provided that can improve durability while reducing manufacturing cost. For this purpose, a fuel supply pump 1 comprises a suction valve 30 and a suction valve stop 32. The suction valve stop 32 regulates a movement of the suction valve 30 in a valve opening direction (a direction in which the suction valve 30 is separated from a seat element 31). The suction valve stop 32 has a disk-shaped section 32d and several plate-shaped sections 32m. The disk-shaped portion 32d has a convex portion 32b that faces the suction valve 30. The plurality of plate-shaped portions 32m support the disc-shaped portion 32d.

Description

Technical area

The present invention relates to a fuel supply pump.

State of the art

In the prior art, various proposals have been made on a flow path structure connecting a suction valve and a pressure chamber with each other. Among these, for example, disclosed JP 2010 - 169080 A a structure in which a plurality of through holes are provided in the circumferential direction of a stopper member of a suction valve to form a flow path to a pressure chamber. Additionally disclosed JP 2013 - 512399 T a structure in which an annular gap is provided on an outer periphery of a suction valve stopper to form a flow path to a pressure chamber.

Citation list

• PTL 1: JP 2010-169080 A
• PTL 2: JP 2013-512399 A

Patent documents

• PTL 1: JP 2010-169080 A
• PTL 2: JP 2013-512399 A

Summary of the invention

Technical problem

Recently, high performance, low fuel consumption and low cost of an internal combustion engine have been vigorously promoted. In response to this, in a fuel supply pump, a large flow rate and a high pressure of the discharged fuel are urgently required for the high performance and the low fuel consumption, an improvement in control accuracy, a reduction in man-hours for the low cost, and the like. In particular, a suction valve is one of the most important parts to achieve this required performance, and improving the performance of the suction valve is an important challenge. Therefore, there is a flow path structure as described in PTL 1 as an example of the large flow rate of the discharged fuel and the improvement in the control accuracy of the flow rate. With this structure, a sufficient flow path cross-sectional area is ensured by providing a plurality of through holes so that a pressure loss before and after the flow path does not increase even if a flow rate of the discharged fuel increases.

In this case, however, the man-hours required for processing increase as the number of the through holes increases, and therefore there is a possibility that the cost increases. In addition, there is a flow path structure as described in PTL 2 as an example of securing the flow path cross-sectional area with a simpler structure.

With this structure, a sufficient cross-sectional flow path area is ensured by turning an outer periphery of a suction valve stopper into an annular passage. Since the suction valve stopper needs to have a function of regulating displacement of a valve body, the valve body needs to be fixed to a pump body or the like. In this case, a repeated load is continuously applied due to an impact of the valve body or the like, and therefore the suction valve stopper is required to have sufficient impact resistance.

However, the structure of PTL 2 does not disclose the method, and there is a possibility that the function as a suction valve stop cannot be sufficiently performed.

An object of the present invention is to provide a fuel supply pump capable of improving durability while reducing manufacturing cost.

Solution to the problem

To achieve the object, according to one aspect of the present invention, there is provided a fuel supply pump comprising: a suction valve; and a suction valve stopper that regulates a movement of the suction valve in a valve opening direction, the suction valve stopper having a disk-shaped portion whose convex portion faces the suction valve and a plurality of plate-shaped portions that support the disk-shaped part.

Advantageous Effects of the Invention

According to the present invention, it is possible to provide a fuel supply pump capable of improving durability and reducing manufacturing cost at the same time. Objects, configurations and effects other than those described above will be clarified from the following description of an embodiment.

Figure list

• [ 1 ] 1 Fig. 13 is a view showing a specific example of a fuel supply pump body.
• [ 2 ] 2 Fig. 13 is a diagram showing an example of an overall configuration of a fuel supply system.
• [ 3 ] 3 Fig. 13 is a view illustrating a fixed state of an assembling root portion (engine side piston mechanism).
• [ 4A ] 4A Fig. 13 is a detailed cross-sectional view (longitudinal cross-sectional view with the valve open) of a suction valve A.
• [ 4B ] 4B Fig. 3 is a detailed cross-sectional view (45 ° cross-sectional view with the valve open) of suction valve A.
• [ 5 ] 5 Figure 3 is a detailed cross-sectional view (with the valve closed) of suction valve A.
• [ 6A ] 6A Figure 4 is a top plan view of a suction valve stop.
• [ 6B ] 6B Figure 3 is a side view of the suction valve stop.
• [ 7th ] 7th Fig. 13 is a view showing a fiber flow line of a protrusion.

Description of embodiments

The following describes the configuration and operation of a fuel supply pump according to an embodiment of the present invention with reference to the drawings. In each drawing, the same reference numbers indicate the same parts.

In the present embodiment, an object, although partially overlapping with the above-mentioned object, is to provide a suction valve stopper capable of securing a sufficient flow path area and at the same time reduced man-hours for processing and a simple structure and sufficient durability against impact forces and to provide an inexpensive fuel supply pump to which the suction valve stop is attached.

(Overall configuration)

2 Fig. 13 is a diagram (schematic diagram) showing an example of the overall configuration of a fuel supply system including a fuel supply pump to which the present invention can be applied. First, the configuration and operation of the entire system are referring to 2 described.

In 2 A portion surrounded by broken lines shows a main body of a fuel supply pump 1 and mechanisms and parts shown in the dashed lines are in a pump body 1P integrated. Fuel is from a fuel tank 20th via a feed pump 21st the pump body 1P is supplied and a pressurized fuel is supplied from the pump body 1P one side of an injector 24 fed. An engine control unit (ECU) 27 serving as a control unit receives a fuel pressure from the pressure sensor 26th and controls the feed pump 21st , an electromagnetic coil 43 in the pump body 1P and the injector 24 to optimize the fuel pressure.

In 2 first becomes a fuel in a fuel tank 20th from the feed pump 21st based on a control signal S1 from the engine control unit 27 (Control unit) pumped up, brought to a suitable delivery pressure and a low pressure fuel suction connection 10a (Suction connection) of the fuel supply pump 1 through a suction pipe 28 fed. The fuel that goes to the low pressure fuel intake port 10a has passed through, reaches a suction port 31b an electromagnetic suction valve 300 constituting a variable capacity mechanism through a pressure pulsation reducing mechanism 9 and a suction channel 10d .

The pressure pulsation reduction mechanism 9 stands with an annular low pressure fuel chamber 7a in connection that increases the pressure by interlocking with a piston 2 changes, which is changed by a cam 93 ( 3 ) of the engine reciprocates, and thus reduces a pulsation of the pressure in the suction port 31b of the suction electromagnetic valve 300.

The one in the suction connection 31b Fuel flowing in the suction electromagnetic valve 300 flows through a suction valve 30th and in a pressure chamber 11 . A valve position of the suction valve 30th is made by controlling the electromagnetic coil 43 in the pump body 1P based on a control signal S2 from the engine control unit 27 (Control unit) determined. In the pressure chamber 11 becomes the power to reciprocate through the cam 93 ( 3 ) the engine on the piston 2 upset.

When the piston 2 reciprocated, the fuel is in a descending stroke of the piston 2 from the suction valve 30th sucked in, the sucked in fuel is in an ascending stroke of the piston 2 pressurized and the fuel becomes a common bar 23 at which the pressure sensor 26th is attached via an exhaust valve mechanism 8th fed under pressure. The injector then injects 24 the fuel based on a control signal S3 from the engine control unit 27 (Control unit) in the engine.

The exhaust valve mechanism 8th at an outlet of the pressure chamber 11 is provided includes an exhaust valve seat 8a , an exhaust valve 8b that with the exhaust valve seat 8a comes into contact and separates from this, an exhaust valve spring 8c, which the exhaust valve 8b towards the exhaust valve seat 8a preloaded, or the like. According to this exhaust valve mechanism 8th becomes the exhaust valve 8b opened when a pressure inside the pressure chamber 11 is higher than a pressure on the exhaust port side 12a on a downstream side of the exhaust valve 8b and the exhaust valve spring 8c overcomes a certain resisting force, and the pressurized fuel becomes out of the pressure chamber 11 the side of the exhaust duct 12a fed and supplied under pressure.

Furthermore, the electromagnetic suction valve 300 of FIG 2 a suction valve 30th , a pole 35 showing a position of the suction valve 30th controls, an anchor section 36 , a suction valve spring 33 , a rod bias spring 40, an armature portion bias spring 41, or the like. According to this mechanism, the suction valve 30th by the suction valve spring 33 biased in the valve closing direction and by the rod biasing spring 40 over the rod 35 preloaded in valve opening direction. Furthermore, the anchor section 36 is biased in the valve closing direction by the armature portion biasing spring 41. The valve position of the suction valve 30th is made by driving the rod 35 through the electromagnetic coil 43 controlled.

As described above, in the fuel supply pump 1 the electromagnetic coil 43 in the pump body 1P by the control signal S2 received from the engine control unit 27 (Control unit) is applied to the electromagnetic suction valve 300, and the fuel supply pump is controlled 1 releases a fuel flow rate so that the fuel that flows through the exhaust valve mechanism 8th the common bar 23 supplied under pressure becomes a desired supply fuel.

Furthermore, the fuel supply pump 1 communication between the pressure chamber 11 and the common bar 23 through a pressure relief valve 100 produced. The pressure relief valve 100 is a valve mechanism that is parallel to the exhaust valve mechanism 8th is arranged. At the pressure relief valve 100 will then when a pressure on the side of the common bar 23 via a set pressure of the pressure relief valve 100 increases, the pressure relief valve 100 opened and the fuel is in the pressure chamber 11 the fuel supply pump 1 and thus an abnormal high pressure condition becomes in the common bar 23 prevented.

The pressure relief valve 100 forms a high pressure flow path 110 showing the exhaust port 12a on the downstream side of the exhaust valve 8b in the pump body 1P and the pressure chamber 11 connects. The exhaust valve 8b is provided so that it is the high pressure flow path 110 bypasses.

The high pressure flow path 110 includes a pressure relief valve 102 that controls a flow of fuel so that the fuel is only in one direction from the outlet flow path to the pressure chamber 11 flows. The pressure relief valve 102 is by a pressure relief spring 105 that generates a compressive force against a pressure relief valve seat 101 pressed and then when a pressure difference between an inside of the pressure chamber 11 and an inside of the high pressure flow path 110 is greater than or equal to a specified pressure which is determined by the pressure relief spring 105, the pressure relief valve is 102 adjusted so that the pressure relief valve 102 from the pressure relief valve seat 101 is disconnected and opened.

In a case where the pressure of the common bar 23 due to a failure of the solenoid suction valve 300 of the fuel supply pump 1 is abnormally high, as a result, when a differential pressure between the high pressure flow path 110 and the pressure chamber 11 greater than or equal to a valve opening pressure of the pressure relief valve 102 is, the pressure relief valve 102 opened, the fuel at an abnormally high pressure comes out of the high pressure flow path 110 into the pressure chamber 11 returned and a high pressure section pipe such as the common ledge 23 is protected.

1 Fig. 13 is a view showing a specific example of the pump body 1P represents that is mechanically integrated. Like it in 1 is shown is the piston 2 that by the cam 93 ( 3 ) of the motor is moved back and forth in a central vertical direction in the drawing (in this case up and down) in a cylinder 6th arranged and the pressure chamber 11 is in the cylinder 6th formed over the piston.

Further, a mechanism on the electromagnetic suction valve 300 side is arranged on a left side in the center of the drawing, and the exhaust valve mechanism 8th is located on a right side in the center in the drawing. There are also low pressure fuel suction ports 10a , the pressure pulsation reduction mechanism 9 , the suction channel 10d or the like arranged on an upper side of the drawing as a mechanism on a fuel suction side. Further, the engine-side piston mechanism (mounting root portion 150 ) on a lower side in the middle of 1 shown.

Like it in 3 as shown, the engine-side piston mechanism is a portion that is embedded and fixed in a main body of an internal combustion engine, and thus is used here as an assembly root portion ( 150 ) designated. The pressure relief valve 100 is in the cross section of 1 not shown. The pressure relief valve 100 can be shown at a different angle within a cross-section, but description and illustration of the pressure relief valve 100 omitted because the pressure relief valve 100 is not directly related to the present invention.

A detailed description of each section of 2 will be given later, and first, the assembly of the mounting root portion will be explained with reference to FIG 3 described. 3 shows a state in which the mounting root portion 150 (Engine-side piston mechanism) is embedded and fixed in the main body of the engine. However, since the description is based on the assembly root section 150 is centered are at 3 Descriptions of other sections are omitted.

In 3 gives a reference number 90 a thick portion of a cylinder head of the internal combustion engine. In the cylinder head 90 the internal combustion engine becomes a mounting hole in advance 95 designed for the mounting root portion. The mounting hole 95 for the mounting root portion has a two-step diameter that is a shape of the mounting root portion 150 corresponds to, and the mounting root portion 150 will be in the mounting hole 95 fitted and arranged for the mounting root portion.

Then the assembly root section becomes 150 airtight to the cylinder head 90 the internal combustion engine fixed. In an arrangement example with airtight fixation of 3 the fuel supply pump is in close contact with a flat surface of the cylinder head 90 the internal combustion engine using a flange 1e attached to the pump body 1P is provided, and is by several bolts 91 fixed. The mounting flange 1e is also on a welded section 1f along the entire circumference on the pump body 1P welded and fixed to form an annular fixing portion. Alternatively, the pump body 1P and the mounting flange 1e be integrated into each other.

In the present embodiment, laser welding is used to perform welding of the welded portion 1f used. There is also an O-ring 61 into the pump body 1P for a seal between the cylinder head 90 and the pump body 1P fitted to prevent engine oil from leaking outside.

The assembly root section 150 , which is fixed and arranged airtight in this way, belongs to a plunger 92 , the rotational movement of a cam attached to a camshaft of the internal combustion engine 93 into vertical movement at a lower end of a small diameter section 2 B of the piston 2 and converts this to the piston 2 transmits. The piston 2 is held by a spring 4 over a holder 15th to the ram 92 crimped. Therefore the piston moves 2 according to the rotation of the cam 93 back and forth.

There is also a piston seal 13 attached to the other end of an inner circumference of a seal holder 7th is held in a state in which it is with the outer periphery of the piston 2 in a lower portion of the cylinder 6th is in sliding contact in the drawing, installed. Accordingly, the fuel in the annular low-pressure fuel chamber 7a even if the piston is sealed 2 slides and the fuel is prevented from leaking outside.

At the same time, lubricating oil (including engine oil) that lubricates a sliding portion in the internal combustion engine is prevented from entering the pump body 1P flows.

Like it in 3 moves in the mounting root portion 150 , which is fixed and arranged airtight, the piston 2 in the assembly root section 150 in the cylinder 6th back and forth according to the rotational movement of the internal combustion engine. An operation of each section associated with this reciprocation will be described with reference to FIG 1 described again. In 1 is the cylinder 6th on the pump body 1P attached to the cylinder 6th guides the reciprocating motion of the piston 2 and one end (upper side in 1 ) of the cylinder 6th is formed in a bottomed tubular shape so that the pressure chamber 11 inside the cylinder 6th is trained.

The pressure chamber also includes 11 an annular groove 6a on an outer peripheral side and multiple communication holes 6b for establishing a connection between the annular groove 6a and the pressure chamber to communicate with the electromagnetic suction valve 300 for supplying the fuel and the exhaust valve mechanism 8th to drain the fuel from the pressure chamber 11 to establish a connection in the outlet duct.

An outer diameter portion of the cylinder 6th is in the pump body 1P pressed in and fixed to this and the cylinder 6th is sealed by a cylindrical press fit surface so that pressurized fuel does not come out of a gap between the pump body 1P and the cylinder 6th emerges on a low pressure side. Further, the small diameter portion is 6c on the outside diameter portion of the cylinder 6th provided on the side of the pressure chamber. The cylinder 6th applies a force to one side of the low pressure fuel chamber 10 off by putting the fuel in the pressure chamber 11 pressurizes but by providing the small diameter portion 1a in the pump body 1P will prevent the cylinder 6th from the side of the low pressure fuel chamber 10 comes out. Surfaces of the pump body 1P and the cylinder 6th are in contact in the axial direction with a flat surface and thus, in addition to sealing the cylindrical press-fit surface (contact cylinder surface) between the pump body 1P and the cylinder 6th also performed a function of a double seal.

A damper cover 14th is on a head of the pump body 1P fixed. The damper cover 14th includes a suction connection 51 and forms the low pressure fuel suction port 10a . The fuel that goes to the low pressure fuel suction port 10a has passed through a suction filter 52 that is in the suction connection 51 is fixed and reaches the suction port 31b of the electromagnetic suction valve 300 via the pressure pulsation reducing mechanism 9 and the suction channel 10d .

The suction filter 52 in the suction connection 51 has the function of preventing between the fuel tank 20th and the low pressure fuel suction port 10a Any foreign matter present will be sucked into the fuel supply pump by the fuel flow.

Because the piston 2 a large diameter section 2a and the small diameter portion 2 B becomes a volume of the annular low pressure fuel chamber 7a enlarged or reduced by the reciprocating movement of the piston. Since the increased / decreased volume via a fuel passage 1d ( 3 ) with the low pressure fuel chamber 10 is in communication, the fuel flows from the annular low pressure fuel chamber 7a into the low pressure fuel chamber 10 when the piston 2 descends, and from the low pressure fuel chamber 10 into the annular low pressure fuel chamber 7a when the piston 2 ascends. As a result, a fuel flow rate into and out of the pump can be decreased during a suction stroke or a return stroke of the pump, and thus a function of reducing pulsation is provided.

The low pressure fuel chamber 10 is with the pressure pulsation reducing mechanism 9 provided that the propagation of the pressure pulsation generated in the fuel supply pump into the intake manifold 28 ( 2 ) decreased.

When the fuel that once in the pressure chamber 11 has flowed through the suction valve 30th , which is again in the open state for capacity control, into the suction channel 10d is returned, the pressure pulsation in the low-pressure fuel chamber 10 by the fuel that is in the suction channel 10d returns, generated.

The one in the low pressure fuel chamber 10 provided pressure pulsation reduction mechanism 9 However, it is formed by a metal damper in which two corrugated disk-shaped metal plates are connected to one another on their outer circumference and into which an inert gas such as argon is fed. Therefore, the pressure pulsation is absorbed and reduced when the metal damper expands and contracts. A reference number 9a is a mounting bracket for fixing the metal damper to an inner peripheral portion of the pump body 1P on and there the mounting bracket 9a is installed in the fuel passage, there are several holes in the mounting bracket 9a provided so that the fluid is free between the front and back of the mounting bracket 9a can flow.

The one at the outlet of the pressure chamber 11 provided exhaust valve mechanism 8th includes the exhaust valve seat 8a , the exhaust valve 8b that with the exhaust valve seat 8a comes into contact and separates from this, the outlet valve spring 8c, which the outlet valve 8b towards the exhaust valve seat 8a preloaded, and an exhaust valve holder 8d holding the exhaust valve 8b and the exhaust valve seat 8a receives, and the exhaust valve seat 8a and the exhaust valve holder 8d are by welding to an abutment section 8e linked together to form the integrated exhaust valve mechanism 8th to build. A stepped section that has an exhaust valve stop 8f (Stop) which forms a stroke of the exhaust valve 8b regulated, is in the exhaust valve holder 8d provided.

In 1 becomes when there is no fuel pressure difference between the pressure chamber 11 and a fuel outlet port 12 consists, the exhaust valve 8b by a biasing force generated by the exhaust valve spring 8c against the exhaust valve seat 8a pressed and is in a closed state. Only when the fuel pressure is in the pressure chamber 11 greater than the fuel pressure in the fuel outlet port 12 is the exhaust valve 8b open against the outlet valve spring 8c and the fuel in the pressure chamber 11 is under high pressure through the fuel outlet port 12 in the common groin 23 drained. When the exhaust valve 8b is opened, the exhaust valve comes on 8b with the exhaust valve stop 8f in contact and the stroke is limited.

Therefore, the lift of the exhaust valve becomes 8b in a suitable manner by the exhaust valve stop 8f certainly. Accordingly, it is possible to prevent the from coming into contact with the fuel outlet port 12 Fuel released at high pressure is returned to the pressure chamber 11 flows because the stroke is too large and the exhaust valve closes 8b is delayed, and it is possible to suppress a decrease in the efficiency of the fuel supply pump. Furthermore, the exhaust valve 8b by an inner peripheral surface of the exhaust valve holder 8d guided so that the exhaust valve 8b only moved in one stroke direction when the exhaust valve 8b is repeatedly opened and closed. In this way the exhaust valve mechanism becomes 8th to a check valve that restricts the direction of fuel flow.

(Structure of the electromagnetic suction valve)

Next, a structure on the electromagnetic suction valve 300 side that is a main part of the present invention will be described with reference to FIG 1 , 4A and 4B described. 4A and 4B Fig. 13 is detailed cross-sectional views (with the valve open) of a suction valve portion A. Here is a longitudinal cross-sectional view in FIG 4A and a 45 ° cross-sectional view in 4B shown.

First, the structure on the electromagnetic suction valve 300 side will be described. The structure on the electromagnetic suction valve 300 side is roughly divided into the suction valve portion A that is mainly the suction valve 30th comprises a magnetic mechanism section B mainly comprising the rod 35 and the anchor section 36 and a coil portion C that mainly comprises the electromagnetic coil 43 includes and is described.

First, the suction valve section A includes the suction valve 30th , a suction valve stop 32 and a suction valve preload spring 33 .

One of these is a seating element 31 formed in a cylindrical shape and has a suction valve seat portion 31a arranged in an inner peripheral side axial direction, and a plurality of suction ports 31b , which lie radially around an axis of the cylinder on.

The suction valve stop 32 is between the pressure chamber 11 and the suction valve 30th arranged and has a disc-shaped portion 32d that with the suction valve 30th overlapped in the axial suction valve direction, and several plate-shaped sections 32m (Projections), the plate-shaped from the disk-shaped portion 32d protrude to the side of the pressure chamber.

The suction valve stop regulates here 32 movement of the suction valve 30th in the valve opening direction (a direction in which the suction valve 30th from the seat element 31 is separated). The multiple plate-shaped sections 32m carry the disc-shaped section 32d .

Because the plate-shaped section 32m is substantially linear, an impact force will come from the suction valve 30th substantially linearly from a root of the plate-shaped portion 32m transferred to a distal end thereof. This makes it possible to prevent the plate-shaped portion from being 32m Gets cracks.

A fixation section 32c (a fixing surface) is on the extreme periphery of the plate-shaped portion 32m and the fixing portion is in a cylindrical inner peripheral surface of a housing portion 31c attached and held there. A support section 32n (a support surface) is at an end surface perpendicular to the fixing portion 32c provided.

In addition, there is a first flow path 32e ( 4B) between an outer peripheral side surface of the disk-shaped portion 32d and the housing section 31c formed on the outer peripheral side from the outer peripheral surface of the disk-shaped portion 32d is arranged. The first flow path 32e is with a second flow path 32f on the pressure chamber side with respect to the pressure chamber side surface of the disk-shaped portion 32d connected and the first flow path 32e and the second flow path 32f are designed to pass through the housing section 31c are continuously connected to each other. Furthermore, the plurality of fixing portions are 32c designed to be on the side of the pressure chamber in relation to a suction valve-side surface of the disc-shaped portion 32d are positioned.

By adopting this configuration, it is possible to form the flow path without performing a drilling operation that requires many man-hours for processing, and it is possible to stop the suction valve 32 on the housing section 31c to fix, which is advantageous in terms of low cost.

The suction valve preload spring 33 is on the inner peripheral side of the suction valve stop 32 and in a pen holder 32h , which is a small diameter portion for partially coaxially stabilizing one end of the spring is arranged. The suction valve 30th is between the suction valve seat portion 31a and the suction valve stop 32 arranged. The suction valve preload spring 33 is a compression coil spring and is installed so that the preload force is applied in a direction in which the suction valve 30th against the suction valve seat portion 31a is pressed. The suction valve preload spring 33 is not limited to the compression coil spring, any shape can be used as long as it can achieve the biasing force, and for example, a leaf spring integrated with the suction valve having a biasing force can be used.

By forming the suction valve portion A in this way, during the suction stroke of the pump, the fuel passed through the suction port 31b ran and got inside, between the suction valve 30th and the suction valve seat portion 31a passes through the outer peripheral side of the suction valve 30th , running (first flow path 32e ) in the circumferential direction between the plate-shaped sections 32m next to the suction valve stop 32 through, passes through the channels of the pump body 1P and of the cylinder and flows into the pressure chamber.

5 shows a detailed cross-sectional view (with the valve closed) of the suction valve section A.

The suction valve seals when the pump discharges 30th the suction valve seat portion 31a by contact and thus has the function of a check valve to prevent the fuel from flowing back to the inlet side.

An axial amount of movement of the suction valve 30th is through the suction valve stop 32 regulated in a finite way.

This is because if the amount of movement is too large, a return flow amount due to a response delay in closing the suction valve 30th increases and the efficiency of the pump is reduced. The regulation of the amount of movement can be done by axial dimensions and fixed positions of the suction valve seat portion 31a , the suction valve 30th and the suction valve stop 32 To be defined.

Like it in 4A and 6A is shown, has the suction valve stop 32 the disc-shaped section 32d with a convex section 32b that the suction valve 30th is facing on. In a state in which the suction valve 30th is open, a downstream surface comes up 30th of the suction valve 30th in contact with the convex portion 32b and thus the movement of the suction valve 30th regulated in the axial direction. Like it in 6A shown is the convex portion 32b on a top surface 32o of the suction valve stop 32 that of the downstream side 30a of the suction valve 30th faces, formed so as to be convex to an upstream side (valve closing direction). A contact area between the downstream side 30th of the suction valve 30th and the top surface 32o of the suction valve stop 32 is made by the convex section 32b decreased. Accordingly, the downstream surface 30a of the suction valve becomes 30th slightly from the top surface 32o of the suction valve stop during the transition from the open state of the valve to the closed state of the valve 32 separated and a valve closing response can be improved. When the annular convex portion 32b is not provided, the contact area increases. Accordingly, a large squeezing force acts between the downstream surface 30a of the suction valve 30th and the top surface 32o of the suction valve stop 32 and the downstream surface 30a of the suction valve 30th is not easily removed from the top surface 32o of the suction valve 32 to separate.

The suction valve 30th , the suction valve seat portion 31a and the suction valve stop 32 repeatedly collide when they work, and thus are made of heat-treated martensitic stainless steel, which has high strength, high hardness and excellent corrosion resistance.

The material of the suction valve stopper is martensitic stainless steel with a carbon content of 0.25% or more, and preferably the hardness after quenching is HRC52 or more. An austenitic stainless material is used for a suction valve spring in consideration of corrosion resistance 33 used. In addition, with regard to a method for fixing the suction valve stop 32 the multiple fixation sections 32c into the inner peripheral surface of the housing section 31c pressed in.

Accordingly, the structure of the suction valve portion A can be simplified by adding several functions in the suction valve stop 32 integrated and the space is used effectively. In addition, the suction valve stop 32 formed by forging, which requires less man-hours for processing than cutting or grinding, and thus it is possible to reduce man-hours for processing, which is advantageous from the viewpoint of low cost.

Furthermore, regarding the arrangement of the fixing portion 32c the multiple fixation sections 32c at a predetermined interval in the circumferential direction on an outer peripheral side of the outermost peripheral end of the outer peripheral surface of the disc-shaped portion 32d arranged (see 6A) and the second flow path 32f becomes on the outer peripheral side of the outermost peripheral end of the outer peripheral side surface of the disk-shaped portion 32d educated. Further, the outermost peripheral end is the outer peripheral surface of the disk-shaped portion 32d configured to be on an outer peripheral side of the outermost peripheral end of the outer peripheral surface of the suction valve 30th is located.

The outermost diameter of the suction valve 30th can be larger than the outermost diameter of the disk-shaped portion 32d .

Accordingly, it is possible to prevent the flow of fuel from the pressure chamber 11 directly on the suction valve 30th hits, which increases the fluid force in the valve closing direction and causes incorrect closing of the valve. As a result, an improvement in the flow rate control accuracy can be achieved.

Next, the magnetic mechanism section B will be described. The magnetic mechanism section B includes the rod 35 which is a movable portion, the anchor portion 36 , a rod guide 37 that is a fixing portion, an outer core 38 , a solid core 39 , the rod bias spring 40 and the armature portion bias spring 41.

The pole 35 which is a movable section, and the anchor section 36 are designed as separate elements. The pole 35 is on an inner peripheral side of the rod guide 37 held displaceably in the axial direction and an inner peripheral side of the armature section 36 is on an outer peripheral side of the rod 35 held movable. That is, both the pole 35 as well as the anchor section 36 are designed so that they can be moved in the axial direction within a geometrically regulated area.

The anchor section 36 has at least one through hole 36a that penetrates in the axial direction of a component for free and smooth movement in the axial direction in the fuel, and movement limitation due to the pressure difference before and after the armature portion is eliminated as much as possible.

The rod guide 37 is designed to be between the outer core 38 that radially into an inner peripheral side of a hole into which the suction valve of the pump body 1P is inserted and rests axially on one end of the suction valve seat, is inserted and on the pump body 1P welded and fixed, and the pump body 1P to be arranged. Like the anchor section 36 also includes the rod guide 37 a through hole 37a which penetrates in the axial direction and is formed so that the armature portion can move freely and smoothly and the pressure of the fuel chamber on the armature portion side does not interfere with the movement of the armature portion.

The outer core 38 has a thin cylindrical shape on a side opposite to the portion to be welded to the fuel supply pump main body, and is welded and fixed so that the solid core 39 is inserted into the inner peripheral side thereof. On an inner peripheral side of the solid core 39 the rod bias spring 40 is arranged to guide the small diameter portion, the rod 35 comes with the suction valve 30th in contact, and the rod biasing spring 40 applies a biasing force in the direction in which the suction valve is removed from the suction valve seat portion 31a is separated, ie in the valve opening direction of the suction valve.

The anchor portion biasing spring 41 is arranged to apply a biasing force to the anchor portion 36 toward a rod flange section 35a exerts while maintaining concentricity by placing one end in a center bearing 37b with a cylindrical diameter is used, which is on a central side of the rod guide 37 is provided. The amount of movement of the anchor section 36 is set to be larger than the amount of movement of the suction valve 30th . This is because the suction valve 30th is securely closed.

There the pole 35 and the rod guide 37 slide towards each other and the rod 35 repeatedly with the suction valve 30th heat-treated martensitic stainless steel is used in consideration of hardness and corrosion resistance. The anchor section 36 and the solid core 39 are made of magnetic stainless steel to form a magnetic circuit, and the rod bias spring 40 and the Armature portion preload springs 41 are made of austenitic stainless steel in consideration of corrosion resistance.

According to the above configuration, the suction valve portion A and the solenoid mechanism portion B are formed so that three springs are organically arranged. The suction valve biasing spring formed in the suction valve portion A. 33 and the rod bias spring 40 and the armature portion bias spring 41 formed in the magnet mechanism portion B correspond to the three springs. In the present embodiment, coil springs are used for all springs, but any springs can be used as long as the preload force can be obtained.

Finally, a configuration of the coil section C will be described. The coil section C includes a first yoke 42 who have favourited Electromagnetic Coil 43 , a second yoke 44 , a bobbin 45 , a connection 46 and a connector 47 . The electromagnetic coil 43 , in which a copper wire several times the coil body 45 is wound is arranged so that it is from the first yoke 42 and the second yoke 44 is surrounded, and is integrally molded and fixed with a connector that is a resin member. One end of each of the two connectors 46 is electrically connected to each end of the copper wire of the coil. The connection is similar 46 integrally formed with the connector so that the other end can be connected to the engine control unit side.

The hole section in the middle of the first yoke 42 of the coil section C is in the outer core 38 pressed in and fixed to this. In this case, an inner diameter side of the second yoke comes 44 with the solid core 39 in contact or comes with easy play to the solid core 39 Near.

In order to form a magnetic circuit and in consideration of corrosion resistance, both the first yoke exist 42 as well as the second yoke 44 Made of a magnetic stainless material and the bobbin 45 is made of a high-strength heat-resistant resin in consideration of the strength properties and heat resistance properties.

By configuring the magnetic mechanism section B and the coil section C as described above, when the magnetic circuit is through the outer core 38 , the first yoke 42 , the second yoke 44 , the solid core 39 and the anchor section 36 is formed and a current is supplied to the coil, a magnetic attraction force between the fixed core 39 and the anchor section 36 and creates a mutual attraction.

In the outer core 38 make the solid core 39 and the anchor section 36 an axial portion in which the magnetic attraction force is mutually generated is as thin as possible, and thus almost all of the magnetic flux flows between the fixed core 39 and the anchor section 36 and the magnetic attraction force can be obtained efficiently.

According to the above-described configuration of the fuel supply pump according to the present embodiment, the pump is operated in a suction stroke, a return stroke, and a discharge stroke as follows.

The suction stroke is described first. The piston is in the suction stroke 2 by the rotation of the cam 93 in 3 in the direction of the cam 93 moves (the piston 2 descends). That is, the position of the piston 2 is shifted from a top dead center to a bottom dead center. In the suction stroke state, refer to, for example 1 a volume of the pressure chamber 11 to and the fuel pressure in the pressure chamber 11 decreases. When the fuel pressure in the pressure chamber 11 in this stroke lower than the pressure in the suction channel 10d is, the fuel flows in the vicinity of the suction valve 30th in the open state, passes through the communication hole 1b that is in the pump body 1P is provided, wherein the annular groove 6a and the communication hole 6b serve as the cylinder outer circumference channel, and flows into the pressure chamber 11 .

The electromagnetic coil remains in place during the suction stroke 43 in the de-energized state and a magnetic bias force does not act. Hence the suction valve 30th by the biasing force of the rod biasing spring 40 from the rod 35 pressed and remains open.

Next, the return stroke will be described. During the return stroke the piston will 2 by the rotation of the cam 93 in 3 moved in an ascending direction. That is, the piston 2 starts moving from the bottom dead center to the top dead center. At this time, the volume of the pressure chamber increases 11 according to the compression movement of the piston 2 after suction, but in this state it passes once into the pressure chamber 11 sucked fuel the suction valve 30th that is in the open state and will again and will enter the suction channel 10d returned and thus the pressure in the pressure chamber does not rise. This stroke is called the return stroke.

When in this state a control signal from the engine control unit 27 (Control unit) is applied to the electromagnetic suction valve 300, the return stroke is shifted to the exhaust stroke.

When the control signal is applied to the electromagnetic suction valve 300, a magnetic attraction force is generated in the coil portion C, and the magnetic attraction force acts on each portion.

In this state, when the magnetic circuit is through the outer core 38 , the first yoke 42 , the second yoke 44 , the solid core 39 and the anchor section 36 is formed and a current is applied to the coil, a magnetic attraction force between the fixed core 39 and the anchor section 36 and creates a mutual attraction. When the anchor section 36 from the solid core 39 that is the fixing portion is tightened, the rod becomes 35 by a locking mechanism of the anchor section 36 and the rod flange portion 35a in one direction from the suction valve 30th moved away. At that time, as it is in 5 shown is the suction valve 30th by the preload force of the suction valve preload spring 33 and a fluid force generated by the in the suction channel 10d flowing fuel is closed.

After the valve has been closed, the fuel pressure in the pressure chamber rises 11 along with the ascending movement of the piston 2 on and when the pressure is greater than or equal to the pressure of the fuel drain connection 12 is high pressure discharge of the fuel through the discharge valve mechanism 8th carried out and the fuel is the common bar 23 fed. This stroke is called the exhaust stroke.

That is, a compression stroke (ascending stroke between a lower starting point and an upper starting point) of the piston 2 includes a return stroke and an exhaust stroke. Then, by controlling a timing for energizing the electromagnetic coil 43 of the electromagnetic suction valve 300, the amount of high pressure fuel discharged can be controlled. When the timing of the excitation of the electromagnetic coil 43 is earlier, in the compression stroke, a portion of the return stroke is small and a portion of the exhaust stroke is large. That is, the one in the suction channel 10d returned fuel decreases and fuel discharged under high pressure increases. If a timing of excitation is delayed during the compression stroke, the proportion of the return stroke is large and the proportion of the exhaust stroke is small. That is, the one in the suction channel 10d returned fuel increases and fuel discharged under high pressure decreases. The timing of the excitation of the electromagnetic coil 43 is by an instruction from the engine control unit 27 (Control unit) controlled.

According to the configuration described above, by controlling the timing of energization of the electromagnetic coil 43 the amount of fuel discharged under high pressure can be controlled to an amount that is required by the internal combustion engine.

The suction, return and pressure operations described above are carried out in an extremely fast cycle.

When a shock frequency between the suction valve 30th and the suction valve stop 32 is high, the frequency reaches hundreds of times per second and an impact load is applied from the support portion at that time 32n the suction valve stop 32 recorded. The thickness and shape of the plate-shaped section 32m accordingly affect the durability performance of the suction valve stop 32 strong.

6A Figure 11 shows a top view of the suction valve stop to explain the thickness and shape and 6B Figure 13 shows a side view of the suction valve stop. The flow path cross-sectional area of the second flow path 32f who is in 4B is shown is around the plate-shaped portion 32m smaller than that of the first flow path 32e and a contribution to the pressure loss is great. By adding a distance H between the root portion of the convex portion 32b and the support section 32n is caused to give the following inequality (1) for a thickness t of the root portion of the convex portion 32b can therefore meet an opening area of the second flow path 32f , which greatly contributes to the pressure loss, can be sufficiently ensured and the pressure loss can be reduced.
[Inequality 1] $$\text{H}>1.4\text{t}$$

That is, the distance H between the surface 32dS of the disk-shaped portion 32d that the suction valve 30th facing, and the distal end of the plate-shaped portion 32m is greater than 1.4 times the thickness t of the disk-shaped portion 32d .

When the plate-shaped section 32m has a stepped shape (step shape), here the mechanical stress is concentrated on a portion with a small curvature when the suction valve 30th and a portion under concentrated stress is easily damaged in the durability test. In addition, cracks are likely to form in a portion with a small curvature during forging, which may also be a factor that deteriorates the performance in the durability test.

Therefore, it is desirable that the plate-shaped portion 32m has a substantially linear shape in which an angular difference θ between the plate-shaped portion 32m and the support section 32n is within a range of the following inequality (2).
[Inequality 2] $$10°<\mathrm{\theta }<60°$$

In other words, the angle (the angular difference θ) of the plate-shaped portion is 32m with respect to the radial direction of the disk-shaped portion 32d 10 ° to 60 °.

Accordingly, the stress concentration when the suction valve collides can be increased 30th can be avoided and the durability performance is improved. Furthermore, it is possible to prevent cracks from occurring during forging.

To the valve closing response of the suction valve 30th To improve, it is effective to have several notches 32p in the convex section 32b formed in a substantially ring shape. That is, it is preferable that the convex portion 32b a ring shape and several notches 32p having. As a result, it is possible to prevent the pen holder 32h has a negative pressure and the valve closing response of the suction valve 30th deteriorated.

According to an experiment conducted by the inventor, it is desirable to make the notch 32p at the root of the plate-shaped section 32m to arrange the valve closing response of the suction valve 30th to improve. In this case, when forming the plate-shaped portion, it is likely that 32m by forging a crack at the root of the convex portion 32b on the side of the notch 32p is formed.

An indented section 32q is provided to prevent the crack. In this case, it is possible to crack the root of the convex portion 32b on the side of the notch 32p to prevent by causing a plate thickness A of the plate-shaped portion 32m and a plate thickness B of the indented portion 32q satisfy the following inequality (3). and the durability performance at the time of the collision of the suction valve 30th and the suction valve stop 32 can be guaranteed.
[Inequality 3] $$\text{B.}>\text{A.}\times 0.6$$

That is, the plate-shaped portion 32m includes the indented section 32q indicating a portion where the plate thickness is thin. The minimum value (plate thickness B) of the plate thickness of the plate-shaped portion 32m is greater than 60% of the maximum value (plate thickness A) of the plate thickness of the plate-shaped portion 32m . A mechanical stress near the root of the convex section 32b is caused by a mechanical tension near the indented section 32q suppressed. As a result, it is possible for cracks to occur at the root of the convex portion 32b to suppress.

The suction valve 30th is off the shelf 35 and the biasing force of the suction valve biasing spring 33 held. When the suction valve preload spring 33 falls down, the return flow rate increases accordingly due to the response delay when the suction valve 30th is closed and the pump output is reduced.

To prevent the suction valve preload spring 33 falls down, therefore, needs to be a distance L from the root portion of the convex portion 32b to a lower surface of the pen holder 32h a relationship of the following inequality (4) with respect to the thickness t of the root portion of the convex portion 32b fulfill.
[Inequality 4] $$\text{L.}>0.5\text{t}$$

That is, the distance L between that of the suction valve 30th facing surface 32dS of the disk-shaped portion 32d and the lower surface of the pen holder 32h (concave portion) is larger than 0.5 times the thickness t of the disc-shaped portion 32d .

However, if the penholder is deepened, cracks are likely to occur in an outer peripheral portion of the lower surface of the penholder when the penholder is formed by forging.

Hence the pen holder 32h through a first inner diameter section 32s with an inner diameter φD1, a second inner diameter portion 32t having an inner diameter φD2 and a third inner diameter portion 32u having an inner diameter φD3 is formed so that the following inequality (5) is satisfied, and it is thus possible to form the spring holder without cracks when the spring holder is formed by forging. Accordingly, it is possible to improve the durability performance of the bias force the suction valve preload spring 33 and the durability performance in collision of the suction valve 30th and the suction valve stop 32 to ensure. [Inequality 5] $$\mathrm{\varphi }\text{D.}1>\mathrm{\varphi }\text{D2}>\mathrm{\varphi }\text{D3}$$

In other words, the disk-shaped section 32d the pen holder 32h (concave portion) on the of the suction valve 30th facing surface 32dS. The inner peripheral surface of the penholder 32h (concave section), in order from the convex section 32b , the first inner diameter section 32s the largest inner diameter, the second inner diameter section 32t an inner diameter smaller than that of the first inner diameter portion 32s and the third inner diameter portion 32u an inner diameter smaller than that of the second inner diameter portion 32t is.

The suction valve preload spring 33 (Feather) is on the lower surface of the feather holder 32h (concave portion) arranged and loads the suction valve 30th in front. The suction valve preload spring 33 is through the third inner diameter section 32u guided.

7th shows the fiber course line of the plate-shaped section 32m . A line that is the root of the convex section 32b and the support section 32n connects with each other is represented by a two-dot chain line.

The fiber flow line near a central portion in a plate thickness direction from the root of the convex portion 32b to the support section 32n and the line making the convex section 32b and the support section 32n connects are essentially parallel to each other.

In other words, there is an inclination of the fiber course line in the middle section between the root and the distal end of the plate-shaped section 32m equal to an inclination of a straight line which is the root of the convex section 32b and the distal end of the plate-shaped portion 32m connects. Furthermore, in a cross section of the suction valve stop 32 through a plane which is an axis of the disk-shaped section 32d contains, an edge 32mE of the plate-shaped portion 32m on one of the suction valve 30th opposite side an S-shaped curve.

As seen in the axial sectional views of 4A and 4B is shown, the disc-shaped portion 32d the suction valve stop 32 of the present embodiment, the top surface 32o. Further, it is desirable that a portion of an extreme diameter portion 32p of the top surface 32o to a most upstream portion 32q of the fixation section 32c (the fixing surface) is formed to be substantially linear. Further, it is on a downstream surface of the plate-shaped portion 32m desirable that a portion of the downstream plate shape forming portion 32s which is the same radial position as that of the extreme diameter section 32p the top surface 32o has to a portion with an innermost diameter 32q of the support section 32n (The support surface) is formed so that it is substantially linear. Further, it is desirable that the linear shape of the outermost diameter portion 32p of the deck 32o to the most upstream portion 32q of the fixation section 32c (the fixing surface) and the linear shape from the downstream plate molding section 32s up to the section with the innermost diameter 32q of the support section 32n (The support surface) are formed so that they are substantially parallel to each other. That is, it is desirable that an upstream surface and a downstream surface of the plate-shaped portion 32m are formed to have the same thickness so that they are substantially parallel to each other.

As a result, the impact load between the suction valve 30th and the suction valve stop 32 efficiently from the convex portion 32b in the direction of the support section 32n dissipated and an excessive stress concentration on the plate-shaped portion 32m can be avoided to ensure the durability performance.

When the configuration of the present embodiment is used, it is generally possible to provide the intake valve stopper in which a sufficient flow path area can be secured by a simple structure that requires few man-hours for processing even if the flow rate of the discharged fuel increases , the pressure loss is prevented from increasing, the flow rate can be controlled with high accuracy, the durability performance in terms of valve strokes can be ensured, and it is possible to provide an inexpensive fuel supply pump to which the suction valve stopper is applied.

As described above, according to the present embodiment, it is possible to improve durability while suppressing manufacturing cost.

It should be noted that the present invention is not limited to the embodiment described above, and various modifications are included. For example, the above embodiment is described in detail in order to clearly explain the present invention, and is not necessarily limited to those having all of the configurations described.

List of reference symbols

1

Fuel supply pump

1P

Pump body

1a

Small diameter section

1b

Communication hole

1e

flange

1f

Welded section

2

piston

2a

Large diameter section

2 B

Small diameter section

6th

cylinder

6a

Groove

6b

Communication hole

6c

Small diameter section

7th

Seal holder

7a

Annular low pressure fuel chamber

8th

Exhaust valve mechanism

8a

Exhaust valve seat

8b

outlet valve

8d

Exhaust valve holder

8e

Abutment section

8f

Exhaust valve stop

9

Pressure pulsation reduction mechanism

9a

Mounting bracket

10

Low pressure fuel chamber

10a

Low pressure fuel suction connection

10d

Suction channel

11

Pressure chamber

12

Fuel outlet connection

12a

Outlet duct

13

Piston seal

14th

Damper cover

15th

holder

20th

Fuel tank

21st

Feed pump

23

Common bar

24

Injector

26th

Pressure sensor

27

Engine control unit

28

Suction pipe

30th

Suction valve

31

Seating element

31a

Suction valve seat portion

31b

Suction connection

31c

Housing section

32

Suction valve stop

32b

Convex section

32c

Fixation section

32d

Disc-shaped section

32e

First flow path

32f

Second flow path

32h

Penholder

32m

Plate-shaped section

32n

Support section

32p

score

32q

Indented section

32s

First inner diameter section

32t

Second inner diameter section

32u

Third inner diameter section

33

Suction valve spring

35

pole

35a

Rod flange section

36

Anchor section

36a

Through hole

37

Rod guide

37a

Through hole

37b

Center bearing

38

Outer core

39

Solid core

42

First yoke

43

Electromagnetic coil

44

Second yoke

45

Bobbin

46

connection

47

Interconnects

51

Suction connection

52

Suction filter

61

O-ring

90

Cylinder head

91

bolt

92

Plunger

93

cam

95

Mounting hole for mounting root section

100

Pressure relief valve

101

Pressure relief valve seat

102

Pressure relief valve

110

High pressure flow path

150

Assembly root section

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• JP 2010 [0002]
• JP 169080 A [0002]
• JP 2013 [0002]
• JP 512399 T [0002]
• JP 2010169080 A [0003]
• JP 2013512399 A [0003]

Claims (18)

A fuel supply pump comprising: a suction valve; and a suction valve stop that regulates a movement of the suction valve in a valve opening direction, wherein the suction valve stop comprises: a disc-shaped portion having a convex portion facing the suction valve, and a plurality of plate-shaped sections that support the disk-shaped section. Fuel supply pump after Claim 1 , wherein an angle of the plate-shaped portion with respect to a radial direction of the disk-shaped portion is 10 ° to 60 °. Fuel supply pump after Claim 2 wherein the plate-shaped portion includes a depressed portion indicating a portion in which a plate thickness is thin, and a minimum value of the plate thickness of the plate-shaped portion is greater than 60% of a maximum value of the plate thickness of the plate-shaped portion. Fuel supply pump after Claim 1 wherein the convex portion has a ring shape and a plurality of notches. Fuel supply pump after Claim 4 , wherein a distance H between a surface of the disc-shaped portion facing the suction valve and a distal end of the plate-shaped portion is greater than 1.4 times the thickness t of the disc-shaped portion. Fuel supply pump after Claim 4 wherein the notch is arranged at a root of the plate-shaped portion. Fuel supply pump after Claim 1 , wherein a material of the suction valve stop is martensitic stainless steel with a carbon content of 0.25% or more, and the hardness of the suction valve stop after quenching is HRC52 or more. Fuel supply pump after Claim 1 wherein the disk-shaped portion on a surface facing the suction valve has a concave portion and an inner peripheral surface of the concave portion in the order starting from the convex portion a first inner diameter portion with the largest inner diameter, a second inner diameter portion with an inner diameter smaller than that of the first Inner diameter portion, and a third inner diameter portion having an inner diameter smaller than that of the second inner diameter portion. Fuel supply pump after Claim 8 , wherein a distance L between a surface of the disk-shaped portion facing the suction valve and a lower surface of the concave portion is greater than 0.5 times the thickness t of the disk-shaped portion. Fuel supply pump after Claim 9 further comprising a spring disposed on the lower surface of the concave portion and biasing the suction valve, the spring being passed through the third inner diameter portion. Fuel supply pump after Claim 1 , wherein a fiber flow line passing through a plate thickness center of the plate-shaped portion is a smooth curve. Fuel supply pump after Claim 11 wherein the grain line passing through the center of the plate thickness of the plate-shaped portion is an S-shaped curve. Fuel supply pump after Claim 12 , wherein an inclination of the fiber course line in a central portion between a root and a distal end of the plate-shaped portion is equal to an inclination of a straight line connecting a root of the convex portion and the distal end of the plate-shaped portion. Fuel supply pump after Claim 1 wherein, in a cross section of the suction valve stop through a plane containing an axis of the disk-shaped portion, an edge of the plate-shaped portion on a side opposite the suction valve is an S-shaped curve. Fuel supply pump after Claim 3 wherein stress in the vicinity of a root of the convex portion is suppressed by stress in the vicinity of the indented portion. Fuel supply pump after Claim 1 wherein the disk-shaped portion of the suction valve stop has a top surface facing a downstream side of the suction valve, and the suction valve stop so is configured to be substantially linear from an extreme diameter portion of the top surface to an upstream most portion of a fixation portion. Fuel supply pump after Claim 16 wherein, on a downstream surface of the plate-shaped portion, the suction valve stop is configured to be substantially linear from a downstream plate shape forming portion having the same radial position as that of the outermost diameter portion of the top surface to an innermost diameter portion of a support portion. Fuel supply pump after Claim 17 wherein the linear shape from the outermost diameter portion of the top surface to the most upstream portion of the fixing portion and the linear shape from the downstream plate shape forming portion to the innermost diameter portion of the support portion are formed to be substantially parallel to each other

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