JP5077775B2 - High pressure pump - Google Patents

High pressure pump Download PDF

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Publication number
JP5077775B2
JP5077775B2 JP2009034768A JP2009034768A JP5077775B2 JP 5077775 B2 JP5077775 B2 JP 5077775B2 JP 2009034768 A JP2009034768 A JP 2009034768A JP 2009034768 A JP2009034768 A JP 2009034768A JP 5077775 B2 JP5077775 B2 JP 5077775B2
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fuel
pressure pump
opening
wall
high
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JP2010190104A (en
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忍 及川
薫 小田
宏史 井上
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株式会社デンソー
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Description

  The present invention relates to a high-pressure pump used in an internal combustion engine (hereinafter referred to as “engine”).

  Conventionally, a fuel supply device that supplies fuel to an engine includes a high-pressure pump that pumps high-pressure fuel. Generally, a high-pressure pump includes a plunger that reciprocates by the rotation of a camshaft.

  Specifically, the stroke of pressurizing the fuel is an intake stroke in which the fuel is sucked from the fuel gallery in the pump into the pressurizing chamber when the plunger moves from the top dead center to the bottom dead center. A metering process for returning a part of the low-pressure fuel to the fuel gallery when going to the point, and a pressurization process for pressurizing the fuel by a plunger toward the top dead center after closing the intake valve. .

  By the way, fuel is normally supplied from the inlet to the fuel gallery, but this supply amount is determined by the pump performance of the low-pressure pump upstream of the high-pressure pump. At this time, if the engine speed increases and the camshaft speed increases, the plunger reciprocates at high speed, so that only the fuel supplied from the inlet can fill the pressure chamber in the intake stroke. There is a risk that the fuel cannot be inhaled.

  As a technique for solving such a problem, a high-pressure pump that performs a pump function even when the plunger moves from top dead center to bottom dead center and sends fuel to the fuel gallery has been proposed (for example, Patent Documents). 1).

JP 2006-200407 A

  However, in Patent Document 1, the flow of fuel in the fuel gallery is not taken into consideration, and there is a possibility that the fuel supplied from the inlet and the fuel sent out by the movement of the plunger interfere with each other in the fuel gallery. If such interference occurs, there is a concern that the intake of fuel into the pressurizing chamber may be hindered.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a high-pressure pump capable of efficiently sucking fuel when sucking fuel with a plunger.

In the high-pressure pump according to claim 1, which is made to achieve the above object, when fuel is supplied from an inlet, the fuel passes through a supply passage, a fuel gallery, a suction valve, and a pressurizing chamber in order. It is discharged from.
The supply passage connects from the inlet to the inlet opening of the fuel gallery. Therefore, the fuel supplied to the inlet is supplied to the fuel gallery through the supply passage.

  The fuel supplied to the fuel gallery is sent from the fuel gallery suction section to the pressurization chamber, and a suction valve is provided halfway to the pressurization chamber. As is well known, this suction valve is closed during the pressurization stroke.

  The fuel is pressurized in the pressurizing chamber. It is the large diameter portion of the plunger that creates the volume change of the pressurizing chamber. This plunger has a large diameter portion and a small diameter portion formed on the opposite side of the pressurizing chamber integrally with the large diameter portion. The fuel pressurized in the pressurizing chamber is discharged from the outlet.

  Under such a basic configuration, in the present invention, the oil seal holder is attached to the housing in correspondence with the plunger. The seal member surrounded by the oil seal holder forms a variable volume chamber around the small diameter portion of the plunger together with the housing described above. The volume chamber passage connects the variable volume chamber to the volume chamber opening of the fuel gallery. At this time, when the volume of the pressurizing chamber decreases due to the movement of the plunger, the volume of the variable volume chamber increases, and fuel is supplied from the fuel gallery to the variable volume chamber. On the other hand, when the volume of the pressurizing chamber increases due to the movement of the plunger, the volume of the variable volume chamber decreases, and fuel is supplied from the variable volume chamber to the fuel gallery.

That is, in the present invention, fuel is supplied to the fuel gallery not only from the inlet opening but also from the volume chamber opening, and the supplied fuel is sent from the suction part of the fuel gallery to the pressurizing chamber.
Particularly in the present invention, when the fuel is supplied from the volume chamber opening, the suppression wall in the fuel gallery suppresses the fuel supply from the inlet opening being inhibited by the flow of fuel generated in the fuel gallery.

  In the state where the plunger reciprocates at high speed, the fuel supplied from the volume chamber opening increases the flow of fuel in the fuel gallery, and when the fuel flows toward the inlet opening, the fuel from the inlet opening There is a risk of hindering supply.

Therefore, in the present invention, a suppression wall is provided between the inlet opening and the volume chamber opening in the fuel gallery, and the fuel gallery flows from the inlet opening due to the flow of fuel flowing from the volume chamber opening to the suction portion via the fuel gallery. The supply of the fuel flowing through the suction portion to the intake is inhibited from being hindered. If it does in this way, in inhaling fuel with a plunger, fuel can be inhaled efficiently.

  As shown in claim 2, the suppression wall is exemplified by an opening edge wall erected on the opening edge of the inlet opening. If it does in this way, possibility that the fuel which goes to an inlet opening will flow the circumference | surroundings of an opening edge wall will become high, and it can suppress that the fuel supply from an inlet opening is obstructed by the flow of fuel.

  Note that if the fuel flowing around the opening edge wall swirls on the downstream side of the opening edge wall, the fuel flow itself may be hindered at the opening edge wall. Therefore, as shown in claim 3, the outer periphery of the opening edge wall may be tapered. Since the outer peripheral portion is tapered, a portion having a large outer diameter is formed on the opening edge wall, so that the flow of fuel around the portion having the large outer diameter can suppress the generation of vortices on the downstream side. As a result, it is possible to suppress the situation where the flow of fuel is inhibited at the opening edge wall.

  Further, as shown in claim 4, the suppression wall is exemplified by a guide wall that guides the fuel supplied from the volume chamber opening to the suction part of the fuel gallery. For example, it may be realized as a plate-like wall extending from the periphery of the volume chamber opening portion toward the suction portion. If it does in this way, possibility that the flow of the fuel which goes to the suction part of a fuel gallery will be created by a guide wall will become high, and can inhale fuel more efficiently.

  Furthermore, as shown in claim 5, the suppression wall is exemplified by a partition wall that suppresses the fuel supplied from the volume chamber opening from flowing to the inlet opening. For example, it may be realized as a plate-like wall that partitions the volume chamber opening and the inlet opening in the fuel gallery. If it does in this way, possibility that the flow of the fuel which goes to an inlet opening will be controlled by a partition wall will become high, and it can control that fuel supply from an inlet opening is inhibited by the flow of fuel.

  By the way, when the structure with which a filter is mounted | worn with an inlet opening part is considered, as shown in Claim 6, it is illustrated that the suppression wall is comprised by a part of filter structural member with which an inlet opening part is mounted | worn. For example, a part of the filter constituent member is protruded from the inlet opening to form the opening edge wall. If it does in this way, since a control wall can be provided using a filter constituent member, the composition and assembly become easy.

  Moreover, you may form a suppression wall separately from a filter structural member. At this time, as shown in claim 7, it is exemplified that the suppression wall is formed by bending the plate-like member. This is because the opening edge wall, the guide wall, and the partition wall can all be realized as plate-like walls. In this way, the processing becomes easier as compared with the case of processing the inside of the fuel gallery.

  Furthermore, as shown in claim 8, it is exemplified that the suppression wall is formed by integral molding of resin. In this way, it is possible to easily manufacture the suppression wall as compared with the case of pressing the metal plate, which is advantageous in terms of cost. Moreover, it contributes to the improvement of assembly performance.

  Since the inlet opening and the volume chamber opening are formed, as shown in claim 8, the suppression wall is positioned by inserting a part of the suppression wall into the volume chamber opening or the inlet opening. It is good also as a structure to be. In this way, for example, even when the restraint wall is formed of a member different from the housing, such as a plate-like member, positioning is facilitated, and as a result, assembly work is facilitated.

  The best mode for carrying out the invention will be described below. In the following, the embodiment of claims 1 and 2 will be referred to as a first embodiment, the embodiment of claims 1, 2, 6, 7, and 9 will be referred to as a second embodiment, and the embodiments of claims 1 to 3 will be described. In the third embodiment, the realization of claims 1, 4 to 7, 9 is referred to as a fourth embodiment, and the realization of claims 1, 2, 4, 5, 7, 9 is referred to as a fifth embodiment. An embodiment of claims 1, 2, 4, 5, 8, and 9 is a sixth embodiment.

It is sectional drawing for demonstrating the basic composition in embodiment of the high pressure pump of this invention. It is sectional drawing which shows the supply channel | path from an inlet, and the return channel | path from a variable volume chamber. It is explanatory drawing which shows typically the III-III sectional view of FIG. It is sectional drawing of the high pressure pump which shows the state which the plunger moved to the top dead center. It is sectional drawing of the high pressure pump which shows the state which the plunger moved to the bottom dead center. (A) is explanatory drawing which shows the opening edge wall of 1st Embodiment, (b) is explanatory drawing which shows the opening edge wall of 2nd Embodiment, (c) is the opening edge of 3rd Embodiment. It is explanatory drawing which shows a wall. (A) is explanatory drawing which shows the guide partition wall of 4th Embodiment, (b) is explanatory drawing which shows the structure of a guide partition wall. It is explanatory drawing which shows the guide partition wall of the modification of 4th Embodiment. (A) is explanatory drawing which shows the guide partition wall of 5th Embodiment, (b) is explanatory drawing which shows the structure of a guide partition wall. It is explanatory drawing which shows the guide partition wall of the modification of 5th Embodiment. It is explanatory drawing which shows the guide partition wall of the modification of 5th Embodiment. It is explanatory drawing which shows the guide partition wall of 6th Embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. Here, the basic configuration of the high-pressure pump will be described first, and then the first to fifth embodiments will be described.
(Basic configuration)
The high-pressure pump of this configuration is as shown in FIG. The high-pressure pump 1 pressurizes fuel supplied from an inlet (not shown) and discharges the fuel from the discharge valve unit 70 to a fuel rail (not shown). A pipe from the low pressure fuel pump is connected to the upstream side of the inlet.
The high-pressure pump 1 includes a main body portion 10, a plunger portion 30, a suction valve portion 50, and a discharge valve portion 70 that constitute an outer shell.

  The main body 10 includes a housing 11 that forms an outer shell. A cover 12 is attached in one direction (upward in FIG. 1) of the housing 11, and a space surrounded by the cover 12 and the housing 11 is a fuel gallery 13. The fuel gallery 13 has a pulsation damper 131 therein. The pulsation damper 131 is disposed with its end portions sandwiched therebetween.

Further, the plunger portion 30 is provided on the opposite side of the cover 12 (downward in FIG. 1). A pressurizing chamber 14 capable of pressurizing fuel is formed near the middle between the plunger portion 30 and the fuel gallery 13.
Furthermore, an intake valve portion 50 (left side in FIG. 1) and a discharge valve portion 70 (right side in FIG. 1) are provided in a direction orthogonal to the arrangement direction of the cover 12 and the plunger portion 30.
With such a configuration, the fuel supplied to the fuel gallery 13 is discharged from the discharge valve portion 70 via the suction valve portion 50 and the pressurizing chamber 14.

Next, the structure of the plunger part 30, the suction valve part 50, and the discharge valve part 70 is demonstrated in detail.
First, the plunger unit 30 will be described.
The plunger unit 30 includes a plunger 31, an oil seal holder 32, a spring seat 33, a plunger spring 34, and the like.

  The plunger 31 has a large-diameter portion 311 supported by a cylinder 15 formed inside the housing 11 and a small-diameter portion 312 having a smaller diameter than the large-diameter portion 311 surrounded by the oil seal holder 32. The large diameter portion 311 and the small diameter portion 312 are integrated and reciprocate in the axial direction in the same phase.

The oil seal holder 32 is disposed at the end of the cylinder 15 and has a base 321 that supports the plunger 31 and a press-fit portion 322 that is press-fitted into the housing 11.
The base 321 is substantially cylindrical. The base portion 321 has a ring-shaped seal 323 therein. The seal 323 adjusts the thickness of the fuel oil film around the small-diameter portion 312 of the plunger 31 and suppresses fuel leakage to the engine. A plunger stopper 324 is disposed on the pressure chamber 14 side adjacent to the seal 323. Further, the base 321 has an oil seal 325 at the tip portion thereof. The oil seal 325 regulates the thickness of the oil film around the small diameter portion 312 of the plunger 31 and suppresses oil leakage.

  The press-fit portion 322 is a portion that protrudes in a cylindrical shape around the base portion 321 and has a U-shaped cross section. On the other hand, a recess 16 corresponding to the press-fit portion 322 is formed in the housing 11. As a result, the oil seal holder 32 is press-fitted in such a manner that the press-fitting portion 322 is pressed against the radially inner wall of the recess 16.

  The spring seat 33 is disposed at the end of the plunger 31. The spring seat 33 is in contact with a cam attached to a camshaft (not shown) with its outer surface in contact with a lifter (not shown) that reciprocates in the axial direction according to the cam profile by the rotation of the camshaft. Thereby, the plunger 31 reciprocates in the axial direction.

  One end of the plunger spring 34 is locked to the spring seat 33, and the other end is locked to the deep portion of the press-fit portion 322 of the oil seal holder 32. Thereby, the plunger spring 34 functions as a return spring of the plunger 31 and urges the lifter 33 to contact the cam surface.

  With this configuration, the reciprocating movement of the plunger 31 according to the rotation of the camshaft is realized. At this time, the volume change of the pressurizing chamber 14 is created by the large diameter portion 311 of the plunger 31.

  In this configuration, in particular, the variable volume chamber 35 is formed around the small diameter portion 312 of the plunger 31. Here, a region surrounded by the cylinder 15 of the housing 11, the base end surface of the large diameter portion 311 of the plunger 31 (step surface with the small diameter portion 312), the outer peripheral wall of the small diameter portion 312, and the seal 323 of the oil seal holder 32. Is the variable volume chamber 35. Although the seal 323 suppresses fuel leakage as described above, the seal 323 seals the variable volume chamber 35 in a liquid-tight manner and prevents fuel leak from the variable volume chamber 35 to the engine. Further, the seal 323 prevents oil leakage from the engine to the variable volume chamber 35.

  The variable volume chamber 35 includes a fuel flow path 326 of the plunger stopper 324, a cylindrical cylindrical flow path 327 formed between the press-fit portion 322 and the concave portion 16 in the radial direction of the press-fit portion 322, and an annular shape formed in the deep portion of the concave portion 16. The fuel is connected to the fuel gallery 13 via the annular flow path 328 and the return flow path 17 (flow path indicated by a broken line in the drawing) formed inside the housing 11.

Next, the suction valve unit 50 will be described.
As shown in FIG. 1, the suction valve unit 50 includes a cylinder part 51 formed by the housing 11, a valve part cover 52 that covers the opening of the cylinder part 51, a connector 53, and the like.
The cylinder part 51 is formed in a substantially cylindrical shape and has a fuel passage 55 inside. A substantially cylindrical seat body 56 is disposed in the fuel passage 55. A suction valve 57 is disposed inside the seat body 56. A spring 58 is accommodated in the intake valve 57.

  A needle 59 is in contact with the suction valve 57. The needle 59 passes through the valve cover 52 described above and extends to the inside of the connector 53. The connector 53 includes a coil 531 and a terminal 532 for energizing the coil 531. Inside the coil 531, a fixed core 533, a movable core 534, and a spring 535 interposed between the fixed core 533 and the movable core 534 are disposed. Here, the needle 59 described above is fixed to the movable core 534. That is, the movable core 534 and the needle 59 are integrated.

  With this configuration, when energization is performed via the terminal 532 of the connector 53, a magnetic attractive force is generated between the fixed core 533 and the movable core 534 by the magnetic flux generated in the coil 531. As a result, the movable core 534 moves toward the fixed core 533, and accordingly, the needle 59 moves away from the pressurizing chamber 14. At this time, the movement of the suction valve 57 is not restricted by the needle 59. Accordingly, the intake valve 57 can be seated on the seat body 56, and the fuel passage 55 and the pressurizing chamber 14 are blocked by the seating of the intake valve 57.

  On the other hand, if energization through the terminal 532 of the connector 53 is not performed, no magnetic attractive force is generated, so that the movable core 534 moves in a direction approaching the pressurizing chamber 14 by the spring 535. Thereby, the needle 59 moves to the pressurizing chamber 14 side. As a result, the movement of the suction valve 57 is regulated by the needle 59, and the suction valve 57 is held on the pressurizing chamber 14 side. At this time, the intake valve 57 is separated from the seat body 56, and the fuel passage 55 and the pressurizing chamber 14 communicate with each other.

Next, the discharge valve unit 70 will be described.
As shown in FIG. 1, the discharge valve portion 70 has a cylindrical accommodating portion 71 formed by the housing 11. A discharge valve 72, a spring 73, and a locking portion 74 are accommodated in a storage chamber 711 formed by the storage portion 71. Further, the opening portion of the storage chamber 711 is a discharge port 75. A valve seat 712 is formed in a deep portion of the storage chamber 711 on the opposite side to the discharge port 75.

  The discharge valve 72 comes into contact with the valve seat 712 by the biasing force of the spring 73 and the pressure from the fuel rail (not shown). Thereby, the discharge valve 72 stops the fuel discharge while the fuel pressure in the pressurizing chamber 14 is low. On the other hand, when the pressure of the fuel in the pressurizing chamber 14 increases and overcomes the urging force of the spring 73 and the pressure from the fuel rail side, the discharge valve 72 moves toward the discharge port 75. As a result, the fuel that has flowed into the storage chamber 711 is discharged from the discharge port 75.

  Next, fuel supply to the fuel gallery 13 will be described. FIG. 2 shows a return passage 17 from the variable volume chamber 35 and a supply passage 18 from the inlet by cutting out a part of the cross section of the high-pressure pump 1 shown in FIG. FIG. 3 is an explanatory view schematically showing a cross section taken along line III-III in FIG. In FIG. 3, only the portion of the fuel gallery 13 is shown.

  As shown in FIG. 3, a volume chamber opening 132 and an inlet opening 133 are formed on the bottom surface of the fuel gallery 13 formed of the housing 11. The return channel 17 (see FIG. 2) described above is connected to the volume chamber opening 132. Further, the supply passage 18 (see FIG. 2) described above is connected to the inlet opening 133. A filter 19 is disposed in the supply passage 18. As a result, the fuel supplied to the inlet via the low-pressure fuel pump (not shown) is supplied to the fuel gallery 13. The fuel gallery 13 is formed with a suction part 134. The fuel sucked from the suction part 134 is sent from the suction valve part 50 to the pressurizing chamber 14.

  Next, the operation of the high-pressure pump 1 will be described. 4 shows a state where the plunger 31 of the plunger unit 30 is at the top dead center, and FIG. 5 shows that the plunger 31 of the plunger unit 30 is at the bottom dead center.

The high-pressure pump 1 operates by repeating an intake stroke, a metering stroke, and a pressurization stroke.
The suction stroke is a stroke for sucking fuel from the fuel gallery 13 into the pressurizing chamber 14. At this time, the plunger 31 moves from the top dead center (see FIG. 4) toward the bottom dead center (see FIG. 5), and the intake valve 57 is in an open state.

The metering process is a process of returning low-pressure fuel from the pressurizing chamber 14 to the fuel gallery 13. At this time, the plunger 31 moves from the bottom dead center (see FIG. 5) toward the top dead center (see FIG. 4), and the suction valve 57 is in an open state.
The pressurizing process is a process of discharging fuel from the pressurizing chamber 14 via the discharge valve unit 70. At this time, the plunger 31 moves toward the top dead center (see FIG. 4), and the suction valve 57 is closed.
4 and 5, all of the intake valves 57 are shown in an open state for convenience.

Here, the function of the variable volume chamber 35 will be described.
In the suction stroke, the volume of the pressurizing chamber 14 increases due to the movement of the plunger 31. On the other hand, the volume of the variable volume chamber 35 decreases. Therefore, the fuel stored in the variable volume chamber 35 is supplied to the fuel gallery 13.
In the metering stroke, the volume of the pressurizing chamber 14 decreases due to the movement of the plunger 31. On the other hand, the volume of the variable volume chamber 35 increases. Therefore, a part of the low-pressure fuel returned from the pressurizing chamber 14 to the fuel gallery 13 is sent to the variable volume chamber 35.

Here, the volume change of the variable volume chamber 35 is caused by the large diameter portion 311 of the plunger 31 as in the pressurizing chamber 14. That is, the volume change of the pressurizing chamber 14 and the volume change of the variable volume chamber 35 occur in the same phase.
In the pressurization stroke, the return of fuel from the pressurization chamber 14 to the fuel gallery 13 is not a problem because the suction valve 57 is closed.

The function of the variable volume chamber 35 provides the following effects.
If the decrease in the volume of the variable volume chamber 35 is “60” in the intake stroke, the fuel of “60” is supplied from the variable volume chamber 35 to the fuel gallery 13. Here, assuming that the increase in the volume of the pressurizing chamber 14 is “100”, the amount of fuel supplied from the inlet opening 133 can be covered by “40”.

  On the other hand, a problem in the metering process is fuel pulsation. If the decrease in the volume of the pressurizing chamber 14 is “100”, a pulsation corresponding to 100 is generated in the fuel gallery 13. When this pulsation propagates from the inlet opening 133 to the supply passage 18, vibration or the like occurs, which causes noise or abnormal noise in the fuel pipe or the like. However, when the increase in the volume of the variable volume chamber 35 is “60”, the pulsation generated in the fuel gallery 13 is suppressed to a value corresponding to “40”.

  Moreover, since the volume change of the pressurizing chamber 14 and the volume change of the variable volume chamber 35 occur in the same phase as described above, an effect can always be obtained regardless of the engine speed.

  Further, the plunger 31 is provided with the small diameter portion 312 to form the variable volume chamber 35. However, when the small diameter portion 312 is sealed with the seal 323 and the oil seal 325, the circumference is larger than when sealing with the large diameter portion. Therefore, an effective seal is realized.

  Furthermore, if the diameter of the small diameter portion 312 is kept as it is and the diameter of the large diameter portion 311 is increased, the discharge amount can be increased. In this case, basically, it is only necessary to design the large-diameter portion 311 and the cylinder 15 on which the large-diameter portion 311 slides, and the discharge amount can be increased by a simple design change.

  In this configuration, the supply passage 18 forms a “supply passage”, the suction valve 57 forms a “suction valve”, the plunger 31 forms a “plunger”, and the discharge port 75 forms an “outlet”. The oil seal holder 32 constitutes an “oil seal holder”, the seal 323 constitutes a “seal member”, and the fuel flow path 326, the cylindrical flow path 327, the annular flow path 328, and the return flow path 17 are “volume chamber passages”. Form.

(First embodiment)
In the high-pressure pump 1 described above, when the plunger 31 reciprocates at a high speed, the fuel supplied from the volume chamber opening 132 increases the flow of fuel in the fuel gallery 13 toward the inlet opening 133. When the fuel flows, there is a possibility that the fuel supply from the inlet opening 133 is hindered.

  Specifically, since the fuel is supplied from the volume chamber opening 132 at a considerably higher rate than the fuel supplied from the inlet opening 133, for example, the fuel that has collided with the pulsation damper 131 is laterally moved in the fuel gallery 13. Easy to make a flow of.

Therefore, in this embodiment, the opening edge wall 135 is erected on the opening edge of the inlet opening 133 as shown in FIG. FIG. 6A shows the vicinity of the inlet opening 133 from the supply passage 18 to the fuel gallery 13. The opening edge wall 135 is a cylindrical wall that surrounds the inlet opening 133. In this way, the possibility that the fuel toward the inlet opening 133 flows around the opening edge wall 135 is high, and it is possible to suppress the fuel supply from the inlet opening 133 from being hindered by the fuel flow. As a result, fuel can be efficiently sucked in the fuel suction stroke by the plunger 31.
In addition, the opening edge wall 135 in this embodiment constitutes an “inhibition wall” and an “opening edge wall”.

(Second Embodiment)
In this embodiment, as shown in FIG. 6B, a part of the constituent members of the filter 82 is an opening edge wall 821. FIG. 6B shows the periphery of the inlet opening 133 from the supply passage 18 to the fuel gallery 13. The opening edge wall 821 is a part of the constituent member of the filter 82 that protrudes from the inlet opening 133 with the filter 82 mounted. Specifically, the end portion is formed by bending a metal plate-like member.
Even if it does in this way, the same effect as the above-mentioned form is produced. In addition, since the opening edge wall 821 is provided by using the constituent members of the filter 82, the configuration and assembly thereof are facilitated.

Further, since the opening edge wall 821 is an end portion formed by bending a metal plate-like member, the processing becomes easier as compared with the case where the inside of the fuel gallery 13 is processed.
Furthermore, the opening edge wall 821 is positioned at the inlet opening 133 by mounting the filter 82. This facilitates positioning even when the opening edge wall 821 is formed of a separate member from the housing.
In addition, the opening edge wall 821 in this embodiment constitutes an “inhibition wall” and an “opening edge wall”.

(Third embodiment)
In this embodiment, as shown in FIG. 6C, the opening edge wall 136 is erected on the opening edge of the inlet opening 133. FIG. 6C shows the vicinity of the inlet opening 133 from the supply passage 18 to the fuel gallery 13. The opening edge wall 136 is a wall surrounding the inlet opening 133, and the outer periphery thereof is formed in a tapered shape.

As a result, there is a high possibility that the fuel toward the inlet opening 133 flows around the opening edge wall 136, and the fuel supply from the inlet opening 133 due to the flow of the fuel can be suppressed. In addition, since the outer peripheral portion is tapered, a portion having a large outer diameter is formed on the opening edge wall 136, so that the flow of fuel around the portion having the large outer diameter can suppress the generation of vortices on the downstream side. . Thereby, the situation where the flow of fuel is inhibited at the opening edge wall 136 can be suppressed. As a result, fuel can be efficiently sucked in the fuel suction stroke by the plunger 31.
In addition, the opening edge wall 136 in this embodiment constitutes an “inhibition wall” and an “opening edge wall”.

(Fourth embodiment)
In this embodiment, as shown in FIG. 7A, a guide partition wall 91 toward the suction part 134 is attached to the volume chamber opening 132. As shown in FIG. 7B, the guide partition wall 91 has an insertion portion 911 that is inserted into the volume chamber opening portion 132. The insertion portion 911 is formed by bending a plate-shaped metal member, and the entire guide partition wall 91 is formed by one plate-shaped member.

  The guide partition wall 91 increases the possibility that a fuel flow toward the suction part 134 of the fuel gallery 13 is created, and allows fuel to be sucked more efficiently. Further, the guide partition wall 91 increases the possibility that the flow of fuel toward the inlet opening 133 is suppressed, and the fuel supply from the inlet opening 133 due to the flow of fuel can be suppressed. As a result, fuel can be efficiently sucked in the fuel suction stroke by the plunger 31.

Further, since the guide partition wall 91 is formed of a plate-like member, the processing becomes easier as compared with the case where the inside of the fuel gallery 13 is processed.
Furthermore, since the guide partition wall 91 has the insertion portion 911 that is inserted into the volume chamber opening portion 132, positioning is facilitated, and assembling work is facilitated.

(Modification of the fourth embodiment)
In this embodiment, as shown in FIG. 8, a guide partition wall 92 toward the suction portion 134 is attached to the inlet opening 133. Also in this case, the guide partition wall 92 has an insertion portion and is formed of a single plate-like member.
Thus, even if the guide partition wall 92 is attached to the inlet opening 133 instead of the volume chamber opening 132, the same effect as described above can be obtained.
In addition, the guide partition walls 91 and 92 in the said form and this form comprise a "suppression wall", a "guide wall", and a "partition wall."

(Fifth embodiment)
In this embodiment, as shown in FIG. 9A, a guide partition wall 93 is attached to the inlet opening 133. As shown in FIG. 9B, the guide partition wall 93 has an insertion portion 931 that is inserted into the inlet opening 133. The insertion portion 931 is formed by bending a plate-shaped metal member, and the entire guide partition wall 93 is formed by a single plate-shaped member. In this case, the guide partition wall 93 has a U-shaped cross section, and a part of the guide partition wall 93 is a wall erected on a part of the opening edge. Such a guide partition wall 93 also provides the same effects as the guide partition walls 91 and 92.

(Modification of the fifth embodiment)
In this embodiment, as shown in FIG. 10, the volume chamber opening 132 is provided closer to the suction part 134 than the inlet opening 133. In this case, providing a guide partition wall 94 that opens on the suction part 134 side is exemplified. In addition, as shown in FIG. 11, when the inlet opening 133 and the volume chamber opening 132 are at the same distance from the suction portion 134, guide partition walls 95 and 96 may be provided on both of them. . In any case, the same effect as described above can be obtained.
In addition, the above-mentioned form and the guide partition walls 93 to 96 of the present embodiment constitute a “suppression wall”, “opening edge wall”, “guide wall”, and “partition wall”.

(Sixth embodiment)
In this embodiment, as shown in FIG. 12A, a guide partition wall 97 toward the suction part 134 is attached to the volume chamber opening 132. As shown in FIG. 12B, the guide partition wall 97 has an insertion portion 971 that is inserted into the volume chamber opening 132. The guide partition wall 97 has the same shape as the guide partition wall 91 (see FIG. 7) in the above embodiment, but differs in that it is integrally formed of resin. Since it is integrally formed of resin, the mating surface of the insertion portion 971 is eliminated as shown in FIGS.

  This guide partition wall 97 increases the possibility that a fuel flow toward the suction part 134 of the fuel gallery 13 will be created, and the fuel can be sucked more efficiently. In addition, the guide partition wall 97 increases the possibility that the flow of fuel toward the inlet opening 133 will be suppressed, and the fuel supply from the inlet opening 133 due to the flow of fuel can be suppressed. As a result, fuel can be efficiently sucked in the fuel suction stroke by the plunger 31.

Further, since the guide partition wall 97 is formed of a plate-like member, the processing becomes easier as compared with the case where the inside of the fuel gallery 13 is processed.
Furthermore, since the guide partition wall 97 has the insertion portion 971 that is inserted into the volume chamber opening portion 132, positioning is facilitated, and as a result, assembly work is facilitated. In particular, since it is formed of resin, it can be easily manufactured as compared with the case where the metal member is bent by press working. This is advantageous in terms of cost. Moreover, it is excellent also in terms of assembly.

  In addition, the guide partition wall 97 in the above embodiment and this embodiment constitutes a “restriction wall”, a “guide wall”, and a “partition wall”.

  As mentioned above, this invention is not limited to the said embodiment at all, In the range which does not deviate from the meaning, it can implement with a various form.

  DESCRIPTION OF SYMBOLS 1 ... High pressure pump, 10 ... Main part, 11 ... Housing, 12 ... Cover, 13 ... Fuel gallery, 131 ... Pulsation damper, 132 ... Volume chamber opening, 133 ... Inlet opening, 134 ... Suction part, 135, 136 DESCRIPTION OF SYMBOLS ... Opening edge wall, 14 ... Pressurizing chamber, 15 ... Cylinder, 16 ... Recess, 17 ... Return flow path, 18 ... Supply passage, 30 ... Plunger part, 31 ... Plunger, 311 ... Large diameter part, 312 ... Small diameter part, 32 ... Oil seal holder, 321 ... Base, 322 ... Press-fit portion, 323 ... Seal, 324 ... Plunger stopper, 325 ... Oil seal, 326 ... Fuel flow path, 327 ... Cylindrical flow path, 328 ... Annular flow path, 33 ... Spring Seat, 34 ... Plunger spring, 35 ... Variable volume chamber, 50 ... Suction valve part, 51 ... Tube part, 52 ... Valve part cover, 53 ... Connector, 531 ... Carp 532 ... Terminal, 533 ... Fixed core, 534 ... Movable core, 535 ... Spring, 55 ... Fuel passage, 56 ... Seat body, 57 ... Suction valve, 58 ... Spring, 59 ... Needle, 70 ... Discharge valve part, 71 ... Accommodating part, 711 ... accommodating chamber, 712 ... valve seat, 72 ... discharge valve, 73 ... spring, 74 ... locking part, 75 ... discharge port (outlet), 82 ... filter, 821 ... opening edge wall, 91, 92, 93, 94, 95, 96, 97 ... guide partition wall, 911, 931, 971 ... insertion part

Claims (9)

  1. A supply passage connecting the inlet from which fuel is supplied to the inlet opening of the fuel gallery,
    A suction valve provided midway from the suction part of the fuel gallery to the pressurizing chamber;
    A large-diameter portion that creates a volume change of the pressurizing chamber, and a plunger that is formed on the opposite side of the pressurizing chamber integrally with the large-diameter portion and has a small-diameter portion smaller than the large-diameter portion;
    An outlet for discharging fuel pressurized in the pressurizing chamber;
    An oil seal holder attached to the housings so as to correspond to said plunger,
    A seal member surrounded by the oil seal holder and forming a variable volume chamber around the small diameter portion together with the housing;
    A volume chamber passage connecting the variable volume chamber to the volume chamber opening of the fuel gallery,
    When the volume of the pressurizing chamber is decreased by the plunger, the volume of the variable volume chamber is increased and fuel is supplied from the fuel gallery to the variable volume chamber, while when the volume of the pressurizing chamber is increased, the variable volume is increased. The volume of the chamber is reduced and fuel is supplied from the variable volume chamber to the fuel gallery.
    The variable upon supply of fuel from the volume chamber to the fuel gallery, the volume chamber in the fuel gallery from the inlet opening by the flow through the opening in the fuel gallery of the fuel flowing through the suction unit via the fuel gallery the restraint wall digits set between the inlet opening and the volume chamber opening in the fuel gallery so to suppress that the supply to the inlet valve of the fuel flowing through the suction unit is inhibited through the A high-pressure pump characterized by that.
  2. The high-pressure pump according to claim 1,
    The high-pressure pump according to claim 1, wherein the suppression wall is configured by an opening edge wall standing on at least a part of an opening edge of the inlet opening.
  3. The high-pressure pump according to claim 2,
    The high-pressure pump characterized in that the outer periphery of the opening edge wall is formed in a tapered shape.
  4. In the high pressure pump according to any one of claims 1 to 3,
    The high-pressure pump, wherein the suppression wall is constituted by a guide wall that guides fuel supplied from the volume chamber opening to the suction part of the fuel gallery.
  5. In the high pressure pump according to any one of claims 1 to 4,
    The high-pressure pump, wherein the suppression wall is constituted by a partition wall that suppresses fuel supplied from the volume chamber opening from flowing to the inlet opening.
  6. In the high-pressure pump according to any one of claims 1 to 5,
    The high-pressure pump, wherein the suppression wall is constituted by a part of a filter constituent member attached to the inlet opening.
  7. In the high pressure pump according to any one of claims 1 to 6,
    The said suppression wall is comprised by bending a plate-shaped member, The high pressure pump characterized by the above-mentioned.
  8. In the high pressure pump according to any one of claims 1 to 6,
    The high pressure pump, wherein the suppression wall is formed by integral molding of resin.
  9. In the high-pressure pump according to any one of claims 1 to 8,
    The suppression wall is positioned by inserting a part of the suppression wall into the volume chamber opening or the inlet opening.
JP2009034768A 2009-02-18 2009-02-18 High pressure pump Expired - Fee Related JP5077775B2 (en)

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JP5077775B2 true JP5077775B2 (en) 2012-11-21

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WO2013035132A1 (en) 2011-09-06 2013-03-14 トヨタ自動車株式会社 Fuel pump, and fuel supply system for internal combustion engine
JP6135437B2 (en) 2013-10-07 2017-05-31 トヨタ自動車株式会社 High pressure fuel pump
JP6260478B2 (en) * 2014-07-10 2018-01-17 株式会社デンソー High pressure pump
JP6361337B2 (en) * 2014-07-10 2018-07-25 株式会社デンソー High pressure pump

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JP4437552B2 (en) * 2006-05-26 2010-03-24 株式会社デンソー High pressure fuel pump
JP2008121469A (en) * 2006-11-09 2008-05-29 Toyota Motor Corp Intake manifold for multi-cylinder engine

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