JP6260478B2 - High pressure pump - Google Patents

Description

  The present invention relates to a high pressure pump.

  Conventionally, a fuel supply system that supplies fuel stored in a fuel tank to at least one of a high-pressure fuel injection valve and a low-pressure fuel injection valve is known. In the fuel supply system, relatively low pressure fuel (hereinafter referred to as “low pressure fuel”) discharged from the low pressure pump is once supplied to the high pressure pump. A part of the low-pressure fuel supplied to the high-pressure pump is pressurized to a desired pressure in accordance with a command from the vehicle control ECU and then supplied to the high-pressure fuel injection valve. It is also supplied to the low pressure fuel injection valve without being pressurized.

  The high-pressure pump includes a plunger, a pressurizing chamber forming member that forms a pressurizing chamber that pressurizes the fuel, a cylinder that accommodates the plunger so as to reciprocate, a fuel adjusting unit that adjusts the amount of fuel pressurized in the pressurizing chamber, And the discharge part etc. which discharge the fuel pressurized in the pressurization chamber to the injection valve for high-pressure fuel are provided. For example, Patent Document 1 describes a high-pressure pump that has a fuel chamber that temporarily stores fuel before being sucked into a pressurizing chamber, and that supplies the fuel stored in the fuel chamber to a low-pressure fuel injection valve. Has been.

JP-T-2006-504903

  However, in the high-pressure pump described in Patent Document 1, regardless of whether the fuel is supplied to the high-pressure fuel injection valve or the low-pressure fuel injection valve, the plunger is driven by the rotational movement of the crankshaft of the internal combustion engine. Move back and forth inside. For this reason, heat due to friction between the plunger and the cylinder accumulates in the high-pressure pump. In the high pressure pump described in Patent Document 1, when fuel is supplied to the high pressure fuel injection valve, the pressure chamber forming member, the cylinder, and the like can be cooled by the fuel passing through the pressure chamber. When the fuel is supplied to the fuel, the fuel flows only in the fuel chamber, so that the pressurizing chamber forming member and the cylinder cannot be sufficiently cooled. For this reason, the fuel sucked into the pressurizing chamber is vaporized by the frictional heat between the plunger and the cylinder, and the fuel may not be pressurized to a desired pressure in the pressurizing chamber. Further, since the cylinder cannot be sufficiently cooled, the liquid fuel that plays a role of lubrication on the sliding surface between the cylinder and the plunger is vaporized. For this reason, the oil film is cut off on the sliding surface, and the cylinder and the plunger may be burned.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a high-pressure pump that prevents the seizure between the cylinder and the plunger while reliably pressurizing the fuel to a desired pressure.

The present invention is a high-pressure pump, and includes a plunger, a cylinder, a pressurizing chamber forming member, a fuel adjusting unit, a discharge unit, an upper pump body, a lower pump body, a pump cover, and guiding means. The plunger is accommodated in the cylinder so as to be reciprocally movable. The pressurizing chamber forming member is provided at the end of the cylinder opposite to the side where the plunger is inserted, and forms a pressurizing chamber that pressurizes fuel when the plunger reciprocates. The fuel adjusting unit adjusts the amount of fuel pressurized in the pressurizing chamber. The discharge unit discharges fuel pressurized in the pressurizing chamber. The upper pump body supports the cylinder and the pressurizing chamber forming member. The lower pump body supports the cylinder and the upper pump body. The pump cover is fixed in a liquid-tight manner to the lower pump body, thereby forming at least a part of the cylinder and forming a main fuel chamber for storing fuel flowing in from the inlet through the periphery of the cylinder . The high-pressure pump according to the present invention is characterized by including guiding means capable of guiding the fuel flowing into the pump cover through the inlet so as to flow around the radial direction of the cylinder in the main fuel chamber .

  In the high-pressure pump of the present invention, the fuel that has flowed into the pump cover is guided by the guiding means to flow around the pressurizing chamber forming member. In the cylinder accommodated in the pump cover, frictional heat is generated by the reciprocating movement of the plunger. The relatively low-temperature low-pressure fuel flowing around the cylinder removes this frictional heat from the cylinder and efficiently cools the cylinder and the pressurizing chamber forming member provided at the end of the cylinder. Thereby, vaporization of the fuel due to frictional heat between the cylinder and the plunger can be prevented, and the fuel can be reliably pressurized to a desired pressure in the pressurizing chamber.

  Further, since the pressurizing chamber forming member can be efficiently cooled by the fuel, it is possible to prevent the fuel flowing on the sliding surface between the cylinder and the plunger from being vaporized by the frictional heat. Thereby, the liquid fuel plays a role of lubrication on the sliding surface between the cylinder and the plunger, and seizure between the cylinder and the plunger can be prevented.

It is sectional drawing of the high pressure pump by 1st embodiment of this invention. It is the II-II sectional view taken on the line of FIG. It is a perspective view of a pump body and a plate-like member of a high-pressure pump by a first embodiment of the present invention. It is sectional drawing of the high pressure pump by 2nd embodiment of this invention. It is sectional drawing of the high pressure pump by 3rd embodiment of this invention. It is sectional drawing of the high pressure pump by 4th embodiment of this invention. It is the VII-VII sectional view taken on the line of FIG. It is the VIII-VIII sectional view taken on the line of FIG. It is a perspective view of a pump body, a partition member, and a plate-like member of a high-pressure pump according to a fourth embodiment of the present invention. It is sectional drawing of the high pressure pump by 5th embodiment of this invention. It is sectional drawing of the high pressure pump by 6th embodiment of this invention. It is sectional drawing of the high pressure pump by 7th embodiment of this invention. It is a perspective view of the spiral member with which the high pressure pump by an eighth embodiment of the present invention is provided.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
The high pressure pump 1 according to the first embodiment pressurizes a relatively low pressure fuel (hereinafter referred to as “low pressure fuel”) pumped up from a fuel tank (not shown) and discharged by a low pressure pump to a relatively high pressure delivery pipe (not shown). Discharge. The fuel accumulated in the high pressure delivery pipe is injected into a cylinder of the internal combustion engine from a high pressure fuel injection valve capable of injecting a relatively high pressure fuel (hereinafter referred to as “high pressure fuel”) connected to the high pressure delivery pipe. The

  As shown in FIG. 1, the high-pressure pump 1 includes a cylinder 10, a pressurizing chamber forming member 12, a plunger 14, a lower pump body 16, an upper pump body 18, a pump cover 30, and a suction valve portion 40 as a “fuel adjusting portion”. And an electromagnetic drive unit 50 and a discharge valve unit 60 as a “discharge unit”.

The cylinder 10 is formed in a cylindrical shape. A columnar plunger 14 is accommodated in the cylinder 10 so as to be reciprocally movable.
The pressurizing chamber forming member 12 is provided so as to block one end of the cylinder 10 at the end of the cylinder 10 opposite to the side where the plunger 14 is inserted. In the high-pressure pump 1 according to the first embodiment, the pressurizing chamber forming member 12 is formed integrally with the cylinder 10. The pressurizing chamber forming member 12 communicates with the pressurizing chamber 120 that pressurizes fuel by the reciprocating movement of the plunger 14, the suction hole 121 that opens in one of the radial directions while communicating with the pressurizing chamber 120, and the pressurizing chamber 120. The other has a discharge hole 122 or the like that opens.
A lower pump body 16 and an upper pump body 18 are provided on the radially outer wall 101 of the cylinder 10 and the pressurizing chamber forming member 12. Hereinafter, the lower pump body 16 and the upper pump body 18 are collectively referred to as “pump body”.

  The lower pump body 16 is a metal member formed in a substantially cylindrical shape. The lower pump body 16 is formed of a flange 161, an upper cylinder 162, a lower cylinder 163, and the like. The flange part 161, the upper cylinder part 162, and the lower cylinder part 163 are integrally formed.

  The flange portion 161 is an annular portion formed so as to extend radially outward of the upper tube portion 162 and the lower tube portion 163. The end portion of the pump cover 30 is fixed to the radially outer end portion of the flange portion 161. The flange portion 161 forms a sub fuel chamber 160 whose volume changes with the reciprocation of the plunger 14 between the lower cylinder portion 163 and an oil seal holder 17 described later. A communication passage 164 that connects the auxiliary fuel chamber 160 and the inside of the pump cover 30 is formed in the flange portion 161. The lower pump body 16 and the oil seal holder 17 correspond to a “sub fuel chamber forming member” recited in the claims.

  The upper cylinder portion 162 is a cylindrical portion provided on one side of the flange portion 161 in the central axis direction, specifically, on the pressure chamber forming member 12 side of the flange portion 161. The cylinder 10 is inserted through the upper cylinder portion 162. The cylinder 10 is fixed to the upper cylindrical portion 162 by press fitting or the like.

  The lower cylinder part 163 is provided on the opposite side of the upper cylinder part 162 with respect to the flange part 161. The lower cylinder portion 163 can be attached to a mounting hole provided in an internal combustion engine (not shown). An oil seal holder 17 is provided at the end of the lower cylinder part 163 opposite to the side connected to the flange part 161 so as to close the opening of the lower cylinder part 163 on the internal combustion engine side. A plunger 14 is inserted through substantially the center of the oil seal holder 17. One end of the first spring 15 is in contact with the oil seal holder 17. The other end of the first spring 15 is in contact with a spring seat 19 fixed to the lower end of the plunger 14. The first spring 15 biases the plunger 14 so as to contact a camshaft (not shown) of the internal combustion engine. The plunger 14 reciprocates in the axial direction of the cylinder 10 along the camshaft profile.

  The upper pump body 18 is formed in a substantially cylindrical shape, and is provided so as to contact an end portion of the upper cylinder portion 162 opposite to the side connected to the flange portion 161. The upper pump body 18 has a through hole 181 substantially at the center. Inserted into the through hole 181 are the pressurizing chamber forming member 12 and the end of the cylinder 10 on the side connected to the pressurizing chamber forming member 12. Further, the upper pump body 18 has a suction valve portion mounting hole 182 and a discharge valve portion mounting hole 183 communicating with the through hole 181. The intake valve portion mounting hole 182 is formed to communicate with the through hole 181 from a direction substantially perpendicular to the central axis of the through hole 181. The discharge valve portion mounting hole 183 is formed so as to communicate with the through hole 181 from the side opposite to the side where the suction valve portion mounting hole 182 is formed, in a direction substantially perpendicular to the central axis of the through hole 181. ing. The upper pump body 18 supports a suction valve portion 40 and a discharge valve portion 60 which will be described later.

  The pump cover 30 is formed in a bottomed cylindrical shape. The end of the pump cover 30 on the opening side is fixed to the lower pump body 16 in a liquid-tight manner. Inside the pump cover 30 is formed a main fuel chamber 300 in which fuel before being sucked into the pressurizing chamber 120 is temporarily stored. The pump cover 30 is provided with a fuel inflow portion 31 (see FIG. 2). A fuel passage 312 included in the fuel inflow portion 31 communicates with an inflow port 311 formed in the outer wall of the pump cover 30.

Inside the pump cover 30, a pulsation damper 32 (see FIG. 1) as a “damper member” and a plate-like member 35 (see FIG. 2) as a “guiding member” and a “shielding member” are provided.
The pulsation damper 32 is formed of two diaphragms 321, 322, an upper fixing member 33, a lower fixing member 34, and the like. The pulsation damper 32 is provided between the upper pump body 18 and the pump cover 30. The two diaphragms 321 and 322 are provided such that the outer edge portions are sandwiched between the upper fixing member 33 and the lower fixing member 34. The two diaphragms 321 and 322 are joined at their outer edges, and a gas of a predetermined pressure is sealed in an inner sealed space. The two diaphragms 321 and 322 reduce the pressure pulsation of the fuel in the main fuel chamber 300 by elastically deforming in the plate thickness direction around the center according to the pressure change of the fuel in the main fuel chamber 300.

  As shown in FIG. 2, the plate-like member 35 is provided between the outer wall 185 of the upper pump body 18 and the inner wall 303 of the pump cover 30 and in the vicinity of the inflow port 311. The plate member 35 is fixed to the outer wall 185 and the inner wall 303. The plate-like member 35 shields the direct fuel flow from the region A30 to the region B30 as a “specific direction” between the region A30 and the region B30 defined by the plate-like member 35. It is induced to flow as indicated by the arrow F shown in FIG.

The intake valve section 40 includes an intake valve body 41, an intake valve seat forming member 42, an intake valve member 43, a stopper member 44, and the like.
The suction valve body 41 is formed in a cylindrical shape, and is fixed to an inner wall that forms the suction valve portion mounting hole 182 of the upper pump body 18. A cylindrical intake valve seat forming member 42 is provided inside the intake valve body 41. The suction chamber 45 formed inside the suction valve seat forming member 42 communicates with the main fuel chamber 300 through a plurality of suction passages 184 formed by the upper pump body 18. The suction valve seat forming member 42 has a valve seat 421 at the opening of the suction chamber 45 on the pressurizing chamber 120 side.

The suction valve member 43 is provided on the pressure chamber 120 side of the valve seat 421 so as to contact or separate from the valve seat 421. The suction valve member 43 can contact the stopper member 44 when being separated from the valve seat 421.
A second spring 47 is provided between the stopper member 44 and the suction valve member 43. The second spring 47 biases the suction valve member 43 so that the suction valve member 43 contacts the valve seat 421.

The electromagnetic drive unit 50 includes a flange 51, a fixed core 52, a movable core 53, a rod 54, a coil 55, a third spring 56, and the like.
The flange 51 is fixed to the outer wall of the intake valve body 41. A movable core 53 is provided inside the suction valve body 41 so as to be reciprocally movable. A rod 54 is fixed at the center of the movable core 53. A guide member 57 fixed to the inside of the suction valve body 41 supports the rod 54 so as to be capable of reciprocating in the axial direction. The third spring 56 biases the rod 54 toward the pressurizing chamber 120 so that the suction valve member 43 is separated from the valve seat 421.

  A fixed core 52 is provided on the side of the movable core 53 opposite to the pressurizing chamber 120 side. A coil 55 is provided on the radially outer side of the fixed core 52. When power is supplied to the coil 55 through the terminal 581 of the connector 58, a magnetic circuit is formed in the movable core 53, the fixed core 52, the flange 51, the yoke 59, etc., and the movable core 53 and the rod 54 are connected to the third spring 56. It is magnetically attracted in the direction of the fixed core 52 against the urging force. On the other hand, when the supply of power to the coil 55 is stopped, the magnetic circuit disappears, and the movable core 53 and the rod 54 are urged toward the pressurizing chamber 120 by the third spring 56.

  The discharge valve portion 60 includes a discharge valve body 61, an intermediate member 62, a discharge valve member 63, a fourth spring 64, a stopper member 65, a relief valve member 66, a fifth spring 67, a spring holder 68, and the like.

  The discharge valve body 61 is a metal member formed in a substantially cylindrical shape. The discharge valve body 61 is fixed to the inner wall forming the discharge valve portion mounting hole 183 of the upper pump body 18. Inside the discharge valve body 61, an intermediate member 62, a discharge valve member 63, a fourth spring 64, a stopper member 65, a relief valve member 66, a fifth spring 67, a spring holder 68 and the like are accommodated.

  The intermediate member 62 is a metal member that is press-fitted and fixed inside the discharge valve body 61. The intermediate member 62 includes communication passages 621 and 622 that allow the discharge valve body 61 to communicate with the pressurization chamber 120 side and the discharge valve body 61 opposite to the pressurization chamber 120. A discharge valve seat 623 that can contact the discharge valve member 63 is formed at the edge of the opening of the communication passage 621 opposite to the pressurizing chamber 120. In addition, a relief valve seat 624 with which the relief valve member 66 can come into contact is formed at the edge of the opening of the communication passage 622 on the pressurizing chamber 120 side.

  The discharge valve member 63 is provided on the opposite side of the intermediate member 62 from the pressurizing chamber 120 so as to be able to reciprocate. The discharge valve member 63 supports one end of a fourth spring 64 that urges the discharge valve member 63 to contact the discharge valve seat 623. When the discharge valve member 63 contacts the discharge valve seat 623, the discharge passage member 621 closes the communication passage 621. When the discharge valve member 63 is separated from the discharge valve seat 623, the discharge passage member 621 opens.

  The stopper member 65 is formed in a bottomed cylindrical shape, and is provided on the opposite side of the discharge valve member 63 from the pressurizing chamber 120. The stopper member 65 supports the other end of the fourth spring 64 that urges the discharge valve member 63 to contact the discharge valve seat 623. The stopper member 65 regulates the position where the discharge valve member 63 can move to the side opposite to the pressurizing chamber 120 while guiding the reciprocating movement of the discharge valve member 63.

  The relief valve member 66 is provided so as to be capable of reciprocating on the pressurizing chamber 120 side of the intermediate member 62. The relief valve member 66 supports one end of a fifth spring 67 that biases the relief valve member 66 against the relief valve seat 624. The relief valve member 66 has a sphere that contacts or separates from the relief valve seat 624. When the spherical body comes into contact with the relief valve seat 624, the communication path 622 is closed, and when separated from the relief valve seat 624, the communication path 622 is opened.

  The spring holder 68 is formed in a bottomed cylindrical shape, and is provided on the pressure chamber 120 side of the relief valve member 66. The spring holder 68 supports the other end of the fifth spring 67. The spring holder 68 has a plurality of communication paths 681 formed in the radial direction. The communication path 681 communicates the inside and the outside of the spring holder 68.

Next, the operation of the high-pressure pump 1 will be described.
(1) Suction stroke When the plunger 14 is lowered from the top dead center toward the bottom dead center by the rotation of the camshaft, the volume of the pressurizing chamber 120 increases and the fuel in the pressurizing chamber 120 is depressurized. At this time, in the discharge valve portion 60, the discharge valve member 63 contacts the discharge valve seat 623 and closes the communication passage 622. On the other hand, in the suction valve section 40, the suction valve member 43 moves toward the pressurization chamber 120 against the urging force of the second spring 47 due to the pressure difference between the pressurization chamber 120 and the suction chamber 45, and the valve is opened. Become. By opening the intake valve portion 40, the fuel in the main fuel chamber 300 flows into the pressurizing chamber 120 through the intake passage 184 and the intake chamber 45.

(2) Metering stroke When the plunger 14 rises from the bottom dead center to the top dead center by the rotation of the camshaft, the volume of the pressurizing chamber 120 decreases. At this time, since the supply of power to the coil 55 is stopped until a predetermined time, the rod 54 presses the suction valve member 43 toward the pressurizing chamber 120 by the urging force of the third spring 56. Thereby, the suction valve part 40 maintains a valve opening state. Since the pressurization chamber 120 and the main fuel chamber 300 are maintained in communication with each other by opening the intake valve section 40, the low-pressure fuel once sucked into the pressurization chamber 120 is returned to the main fuel chamber 300 and pressurized. The fuel pressure in the chamber 120 does not increase.

  Electric power is supplied to the coil 55 at a predetermined time while the plunger 14 is rising from the bottom dead center toward the top dead center. A magnetic attractive force is generated between the fixed core 52 and the movable core 53 by the magnetic field generated by the coil 55 to which power is supplied. When the generated magnetic attractive force becomes larger than the difference between the urging force of the second spring 47 and the urging force of the third spring 56, the movable core 53 moves to the fixed core 52 side. Thereby, the pressing force of the rod 54 against the suction valve member 43 is released.

  The suction valve member 43 with the pressing force of the rod 54 released follows the operation of the rod 54 by the urging force of the second spring 47 and the dynamic pressure of the low-pressure fuel discharged from the pressurizing chamber 120 to the suction chamber 45. Then, it moves in the valve closing direction and comes into contact with the valve seat 421. Thereby, the pressurizing chamber 120 and the suction chamber 45 are shut off.

(3) Discharge stroke After the suction valve member 43 is closed, the fuel pressure in the pressurizing chamber 120 increases as the plunger 14 rises. When the force acting on the discharge valve member 63 due to the fuel pressure in the pressurizing chamber 120 becomes larger than the sum of the force acting on the discharge valve member 63 due to the fuel pressure on the fuel outlet side and the biasing force of the fourth spring 64, The discharge valve member 63 is opened. Thereby, the high-pressure fuel pressurized in the pressurizing chamber 120 is discharged toward the high-pressure fuel injection valve.
Note that the supply of power to the coil 55 is stopped during the discharge stroke. Since the force that the pressure of the fuel in the pressurizing chamber 120 acts on the suction valve member 43 is larger than the urging force of the third spring 56, the suction valve member 43 maintains the closed state.
In this way, the high-pressure pump 1 repeats the intake stroke, the metering stroke, and the discharge stroke, and pressurizes and discharges an amount of fuel necessary for the internal combustion engine.

  In the high-pressure pump 1 according to the first embodiment, the fuel sucked into the pressurizing chamber 120 first flows from the inlet 311 into the main fuel chamber 300 inside the pump cover 30. A plate-like member 35 is provided in the vicinity of the inflow port 311. The fuel flowing into the main fuel chamber 300 from the inflow port 311 is guided to flow around the cylinder 10 by the plate member 35 as indicated by an arrow F shown in FIG. Since the cylinder 10 accommodated in the main fuel chamber 300 generates frictional heat due to the reciprocating movement of the plunger 14, it becomes a relatively high temperature. Therefore, in the high-pressure pump 1 according to the first embodiment, the frictional heat accumulated in the cylinder 10 and the like is deprived by the relatively low-temperature low-pressure fuel flowing around the pump body that houses the cylinder 10 and the pressurizing chamber forming member 12. 10 and the pressurizing chamber forming member 12 are efficiently cooled. Accordingly, it is possible to prevent the fuel in the pressurizing chamber 120 from vaporizing due to frictional heat between the cylinder 10 and the plunger 14 and to reliably pressurize the fuel to a desired pressure in the pressurizing chamber 120.

Conventionally, in the high pressure pump, fuel leaks from the pressurizing chamber toward the sub fuel chamber along the sliding surface between the cylinder and the plunger. The leaked liquid fuel plays a role of lubrication on the sliding surface between the cylinder and the plunger. If the fuel on the lubricating surface is vaporized, the cylinder and the plunger may be burned.
In the high-pressure pump 1 according to the first embodiment, the liquid fuel flowing along the sliding surface between the cylinder 10 and the plunger 14 is vaporized in order to efficiently cool the cylinder 10 and the like by the low-pressure fuel flowing around the pump body. Can be prevented. Thereby, seizure of the cylinder 10 and the plunger 14 can be prevented, and damage to the high-pressure pump 1 can be prevented.

  The high-pressure pump 1 according to the first embodiment includes a pulsation damper 32. Thereby, the pressure pulsation of the fuel in the main fuel chamber 300 can be reduced.

  In addition, the high-pressure pump 1 according to the first embodiment has a sub fuel chamber 160. Thereby, the pressure pulsation of the fuel in the main fuel chamber 300 can be reduced, the amount of fuel that can be supplied to the pressurizing chamber 120 can be increased, and the suction efficiency of the high-pressure pump 1 can be improved.

(Second embodiment)
Next, a high-pressure pump according to a second embodiment of the present invention will be described with reference to FIG. The second embodiment is different from the first embodiment in that a fuel outlet is provided in the pump cover. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  In the high pressure pump 2 according to the second embodiment, the pump cover 30 is provided with a fuel outflow portion 36 that flows out to a low pressure delivery pipe (not shown) without pressurizing the low pressure fuel supplied from the low pressure pump in the pressurization chamber 120. That is, the high-pressure pump 2 is provided so that fuel can be supplied to each of a high-pressure fuel injection valve capable of injecting high-pressure fuel and a low-pressure fuel injection valve capable of injecting low-pressure fuel.

  The fuel outflow portion 36 forms an outflow passage 362 communicating with the inside of the low pressure delivery pipe. The outflow passage 362 communicates with the main fuel chamber 300 via an outflow port 361 formed in the outer wall of the pump cover 30.

  The plate-like member 35 is fixed to the inner wall 303 of the pump cover 30 and the outer wall 185 of the pump body between the part where the inlet 311 is formed and the part where the outlet 361 is formed. As a result, the low-pressure fuel flowing into the main fuel chamber 300 from the inlet 311 is guided to flow around the pump body that houses the cylinder 10 and the pressurizing chamber forming member 12 as indicated by an arrow F shown in FIG. . Part of the induced low pressure fuel is supplied to the low pressure delivery pipe through the outlet 361 without being pressurized by the high pressure pump 2.

  As shown in FIG. 4, the communication passage 164 that connects the main fuel chamber 300 and the sub fuel chamber 160 is formed on the outflow port 361 side and in the vicinity of the outflow port 361 as seen from the plate-like member 35. .

  In the high-pressure pump 2 according to the second embodiment, the fuel supplied to the low-pressure fuel injection valve is once supplied to the high-pressure pump 2. The low pressure fuel supplied to the high pressure pump 2 flows around the pump body that accommodates the cylinder 10 and the pressurizing chamber forming member 12 in the main fuel chamber 300. A part of the low-pressure fuel flowing around the pump body is sucked into the pressurizing chamber 120 through the suction passage 184, and the other flows out toward the low-pressure fuel injection valve through the outlet 361. Thereby, even when the high-pressure pump 2 does not supply fuel to the high-pressure fuel injection valve, the cylinder 10 or the like that becomes relatively hot due to the reciprocating movement of the plunger 14 can be cooled by the low-pressure fuel supplied to the low-pressure fuel injection valve. it can. Therefore, the second embodiment has the same effect as the first embodiment, and can cool the cylinder 10 and the like more efficiently.

  In the high-pressure pump 2, a communication passage 164 that communicates the main fuel chamber 300 and the sub fuel chamber 160 is formed on the outflow port 361 side and in the vicinity of the outflow port 361 when viewed from the plate-like member 35. As a result, when the fuel in the auxiliary fuel chamber 160 is at a relatively high temperature, the fuel in the auxiliary fuel chamber 160 flowing into the main fuel chamber 300 through the communication passage 164 quickly passes through the outlet 361 and flows into the pump cover 30. Can flow out. Therefore, the temperature of the fuel in the main fuel chamber 300 can be prevented from rising due to the fuel in the sub fuel chamber 160, and the cylinder 10 and the like can be reliably cooled.

(Third embodiment)
Next, a high-pressure pump according to a third embodiment of the present invention will be described with reference to FIG. The third embodiment is different from the second embodiment in the position at which the communication path that connects the main fuel chamber and the sub fuel chamber is formed. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 2nd embodiment, and description is abbreviate | omitted.

  In the high-pressure pump 3 according to the third embodiment, the communication passage 165 that communicates the main fuel chamber 300 and the sub fuel chamber 160 is on the inlet 311 side as viewed from the plate-like member 35 as shown in FIG. 311 is formed in the vicinity.

  In the high-pressure pump 3 according to the third embodiment, the low-pressure fuel supplied to the low-pressure fuel injection valve flows around the pump body that accommodates the cylinder 10 and the pressurizing chamber forming member 12 in the main fuel chamber 300. A part of the low-pressure fuel flowing around the pump body is sucked into the pressurizing chamber 120 through the suction passage 184, and the other flows out toward the low-pressure fuel injection valve through the outlet 361. Thereby, 3rd embodiment has the same effect as 1st embodiment.

  In the high-pressure pump 3, a communication passage 165 that connects the main fuel chamber 300 and the sub fuel chamber 160 is formed on the inlet 311 side and in the vicinity of the inlet 311 when viewed from the plate-like member 35. Thereby, when the fuel in the auxiliary fuel chamber 160 is at a relatively low temperature, the cylinder 10 and the like can be cooled using the fuel in the auxiliary fuel chamber 160 flowing into the main fuel chamber 300 through the communication path 165. Therefore, the cylinder 10 can be cooled more efficiently.

(Fourth embodiment)
Next, a high pressure pump according to a fourth embodiment of the present invention will be described with reference to FIGS. The fourth embodiment is different from the second embodiment in that a partition member that partitions the inside of the pump cover is accommodated. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 2nd embodiment, and description is abbreviate | omitted.

In the high-pressure pump 4 according to the fourth embodiment, an annular member 37 as a “partition member” is provided inside the pump cover 30.
The annular member 37 is a substantially annular flat plate member, and is supported by the end of the upper pump body 18 on the pulsation damper 32 side, as shown in FIG. The annular member 37 divides the interior of the pump cover 30 into a first fuel chamber 301 communicating with the inlet 311 and the outlet 361 and a second fuel chamber 302 in which the pulsation damper 32 is accommodated. The first fuel chamber 301 and the second fuel chamber 302 communicate with each other via a gap between the radially outer end of the annular member 37 and the inner wall 303 of the pump cover 30. The first fuel chamber 301 accommodates the upper pump body 18, a part of the lower pump body 16, a part of the cylinder 10, the pressurizing chamber forming member 12, and the like. A pulsation damper 32 is accommodated in the second fuel chamber 302.

  In the high-pressure pump 4 according to the fourth embodiment, the low-pressure fuel flowing into the first fuel chamber 301 from the inlet 311 flows around the pump body by the plate-like member 35 as shown by the arrow F in FIG. As a result, the flow to the second fuel chamber 302 is partly interrupted, so that it stays in the first fuel chamber 301 for a relatively long time. Accordingly, the fourth embodiment has the same effects as the first embodiment, and can cool the cylinder 10 and the like more efficiently by the low-temperature low-pressure fuel that stays for a relatively long time.

(Fifth embodiment)
Next, a high-pressure pump according to a fifth embodiment of the present invention will be described with reference to FIG. The fifth embodiment is different from the second embodiment in that the plate-like member is not provided and the direction in which the inflow passage forming member is attached. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 2nd embodiment, and description is abbreviate | omitted.

  The high-pressure pump 5 according to the fifth embodiment includes a fuel inflow portion 71 as “guidance means” and “external inflow passage forming member”. The fuel inflow portion 71 forms an external inflow passage 712 that communicates with an inflow port 711 of the pump cover 30.

  The fuel inflow portion 71 is provided such that its central axis CA71 is in a twisted position with respect to the central axis CA10 of the cylinder 10. Specifically, as shown in FIG. 10, assuming a virtual circle VC10 centered on a point on the central axis CA10 of the cylinder 10, the central axis CA71 of the fuel inflow portion 71 extends in the tangential direction of the virtual circle VC10. It is formed as follows. Further, the inner wall forming the inflow port 711 is formed substantially parallel to the central axis CA71.

  In the high pressure pump 5 according to the fifth embodiment, the low pressure fuel flowing through the external inflow passage 712 flows into the main fuel chamber 300 through the inflow port 711. Since the low-pressure fuel flowing through the external inflow passage 712 is guided to flow in the tangential direction of the virtual circle VC10 as indicated by an arrow F in FIG. 10, it flows around the pump body in the main fuel chamber 300. Thereby, 5th embodiment has the same effect as 1st embodiment.

(Sixth embodiment)
Next, a high pressure pump according to a sixth embodiment of the present invention will be described with reference to FIG. The sixth embodiment is different from the second embodiment in that a plate-like member is not provided and a flow path forming member is provided inside the pump cover. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 2nd embodiment, and description is abbreviate | omitted.

In the high-pressure pump 6 according to the sixth embodiment, an internal flow path forming member 81 as “guidance means” is provided inside the pump cover 30.
The internal flow path forming member 81 is provided on the inner side of the part where the inlet 311 of the pump cover 30 is formed. The internal flow path 811 formed by the internal flow path forming member 81 communicates with the inlet 311 and the main fuel chamber 300 as shown in FIG. The opening 813 on the inner side of the pump cover 30 of the internal flow path 811 is formed in a direction different from the direction of the central axis CA10 of the cylinder 10 when viewed from the internal flow path forming member 81. Thereby, the low-pressure fuel passing through the opening 813 is formed to change the flow in a direction along the inner wall 303 of the pump cover 30.

  In the high pressure pump 6 according to the sixth embodiment, the low pressure fuel passing through the inflow port 311 flows along the inner wall 303 of the pump cover 30 as shown by an arrow F in FIG. As a result, the low-pressure fuel flows around the pump body in the main fuel chamber 300. Therefore, the sixth embodiment has the same effect as the first embodiment.

(Seventh embodiment)
Next, a high pressure pump according to a seventh embodiment of the present invention will be described with reference to FIG. The seventh embodiment is different from the first embodiment in that the plate-like member is not provided and the position where the inflow passage forming member is provided. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  As shown in FIG. 12, the fuel inflow portion 91 as the “guidance means” and “external inflow passage forming member” of the high pressure pump 7 according to the seventh embodiment is a suction passage of the upper pump body 18 with the cylinder 10 interposed therebetween. It is provided on the side opposite to the position where 184 is formed. An external inflow passage 912 formed by the fuel inflow portion 91 communicates with the inside of the pump cover 30 via an inflow port 911 included in the pump cover 30.

  In the high-pressure pump 7 according to the seventh embodiment, the low-pressure fuel flowing into the main fuel chamber 300 through the inflow port 911 flows around the pump body toward the suction passage 184 as indicated by an arrow F in FIG. The low-pressure fuel that flows around the pump body is sucked into the pressurizing chamber 120 through the suction passage 184. Thereby, 7th embodiment has the same effect as 1st embodiment.

(Eighth embodiment)
Next, a high pressure pump according to an eighth embodiment of the present invention will be described with reference to FIG. The eighth embodiment differs from the first embodiment in that a spiral member is provided instead of the plate member. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  The high-pressure pump according to the eighth embodiment accommodates a spiral member 96 as “guidance means” shown in FIG. One end 961 of the spiral member 96 is provided in the vicinity of the inflow port 311. The other end 962 is provided in the vicinity of the pulsation damper 32. The low pressure fuel flowing into the main fuel chamber 300 from the inlet 311 accommodates the cylinder 10 and the pressurizing chamber forming member 12 from one end 961 toward the other end 962 along the shape of the spiral member 96. It flows while rotating around the pump body. In FIG. 13, the position of the cylinder 10 with respect to the spiral member 96 is indicated by a two-dot chain line.

  In the high pressure pump according to the eighth embodiment, the low pressure fuel flowing into the main fuel chamber 300 through the inlet 311 flows through the main fuel chamber 300 along the shape of the spiral member 96. As a result, the low-pressure fuel flows around the pump body. Therefore, the eighth embodiment has the same effect as the first embodiment.

(Other embodiments)
(A) In the above-described embodiment, the pulsation damper is accommodated inside the pump cover. However, the pulsation damper is not necessary.

  (A) In the first embodiment, the communication passage that communicates the main fuel chamber and the sub fuel chamber is formed on the outflow side as viewed from the plate-like member and in the vicinity of the outflow port. However, the position where the communication path is formed is not limited to this.

  (C) In the fourth embodiment, the partition member is supported by the end of the upper pump body on the pulsation damper side. However, the site | part which supports a division member is not limited to this. It may be fixed to the pump cover, or may be fixed to the pulsation damper.

  (D) In the first embodiment, the plate-like member is provided in the vicinity of the inflow port. In the second to fourth embodiments, the plate-like member is provided between a portion where the inflow port is formed and a portion where the outflow port is formed. However, the position where the plate-like member is provided is not limited to this. What is necessary is just to provide so that the fuel flow between a pair of adjacent area | regions inside a pump cover may be interrupted | blocked so that the fuel which flows in into the inside of a pump cover may flow around a cylinder.

  (E) In the fifth embodiment, the central axis of the fuel inflow portion is provided so as to extend in the tangential direction of a virtual circle centered on a point on the central axis of the cylinder. However, the position where the fuel inflow portion is provided is not limited to this. The fuel inflow portion may be provided so that the center axis of the fuel inflow portion and the center axis of the cylinder are in a twisted position.

  (F) In the seventh embodiment, the fuel inflow portion is provided on the side opposite to the suction passage. However, the position where the fuel inflow portion is provided is not limited to this. It may be provided at a position away from the intake passage and at a position where the time in which the fuel in the main fuel chamber stays around the pump body is relatively long.

  (G) In the first, third, fifth to eighth embodiments, an annular member as a “partition member” that divides the inside of the pump cover into a first fuel chamber and a second fuel chamber is not provided. However, a “compartment member” may be provided in these embodiments.

  As mentioned above, this invention is not limited to such embodiment, It can implement with a various form in the range which does not deviate from the summary.

1, 2, 3, 4, 5, 6 ... high pressure pump,
10 ... Cylinder,
12: Pressurizing chamber forming member,
120 ... pressurization chamber,
14: Plunger,
30 ... pump cover,
311, 711 ... inlet,
35 ... Plate-like member (guidance means, shielding member)
40 ・ ・ ・ Suction valve part (fuel adjusting part),
50 ... Electromagnetic drive unit (fuel adjustment unit),
60 ... discharge valve part (discharge part).

Claims (14)

A plunger (14);
A cylinder (10) for accommodating the plunger in a reciprocating manner;
A pressurizing chamber forming member (12) provided at an end of the cylinder opposite to the side where the plunger is inserted, and forming a pressurizing chamber (120) that pressurizes fuel when the plunger reciprocates;
A fuel adjuster (40, 50) for adjusting the amount of fuel pressurized in the pressurizing chamber;
A discharge section (60) for discharging fuel pressurized in the pressurizing chamber;
An upper pump body (18) for supporting the cylinder and the pressurizing chamber forming member;
A lower pump body (16) supporting the cylinder and the upper pump body;
A main fuel chamber (300) which is fixed in a liquid-tight manner to the lower pump body, accommodates at least a part of the cylinder, and stores fuel flowing in from the inflow ports (311, 711, 911 ) is formed around the cylinder. A pump cover (30) to
Guiding means (35, 71, 81, 91, 96) capable of guiding the fuel flowing into the inside of the pump cover through the inlet to flow around the radial direction of the cylinder in the main fuel chamber ;
A high-pressure pump (1, 2, 3, 4, 5, 6, 7) characterized by comprising:   The high-pressure pump according to claim 1, further comprising a damper member (32) accommodated inside the pump cover.   3. The high-pressure pump according to claim 1, wherein the pump cover has an outlet (361) through which fuel inside the pump cover flows out. 4.   A first fuel chamber (301) that communicates the interior of the pump cover with the inflow port and houses at least a part of the pressurizing chamber forming member, and a second fuel chamber (302) that communicates with the first fuel chamber. The high-pressure pump according to any one of claims 1 to 3, further comprising a partition member (37) partitioning into two.   The auxiliary fuel chamber forming member (16, 17) which communicates with the inside of the pump cover and forms an auxiliary fuel chamber (160) whose volume changes as the plunger reciprocates is provided. The high-pressure pump according to any one of the above.   The guide means is a shielding member (35) that is housed in the pump cover and is provided between the inner wall (303) of the pump cover and the pressurizing chamber forming member to shield the flow of fuel in a specific direction. The high-pressure pump according to any one of claims 1 to 5, wherein A sub fuel chamber forming member that communicates with the inside of the pump cover and forms a sub fuel chamber whose volume changes as the plunger reciprocates;
The high-pressure pump according to claim 6, wherein an opening of the communication passage (165) that communicates the inside of the pump cover and the auxiliary fuel chamber is formed on the inlet side when viewed from the shielding member. The pump cover has an outlet (361) through which fuel inside the pump cover flows out,
The shielding member is provided between the inner wall between the portion where the inlet of the pump cover is formed and the portion where the outlet of the pump cover is formed, and the pressurizing chamber forming member. The high-pressure pump according to claim 6. A sub fuel chamber forming member that communicates with the inside of the pump cover and forms a sub fuel chamber whose volume changes as the plunger reciprocates;
9. The high-pressure pump according to claim 8, wherein an opening of the communication passage (164) that communicates the inside of the pump cover and the auxiliary fuel chamber is formed on the outlet side as viewed from the shielding member. The guide means is an external inflow passage forming member (71) that forms an external inflow passage (712) communicating with the inflow port outside the pump cover,
The high-pressure pump according to any one of claims 1 to 5, wherein the central axis (CA71) of the external inflow passage forming member is in a twisted position with respect to the central axis (CA10) of the cylinder. .   The high-pressure pump according to claim 10, wherein the external inflow passage allows fuel to flow into the pump cover from a tangential direction of a virtual circle (VC10) centered on a point on a central axis of the cylinder. . The guide means is an internal flow path forming member (81) that forms an internal flow path (811) communicating with the inflow port inside the pump cover,
The opening (813) of the internal flow path that the internal flow path forming member has on the inner side of the pump cover is formed in a direction different from the direction of the central axis of the cylinder as viewed from the internal flow path forming member. The high pressure pump according to claim 1, wherein the high pressure pump is provided. The fuel adjustment unit has a suction passage (184) for sucking the fuel inside the pump cover and leading it to the pressurizing chamber,
The guiding means is an external inflow passage forming member (91) that forms an external inflow passage (912) communicating with the inflow port provided on the opposite side of the suction passage with the pressurizing chamber forming member interposed therebetween. The high-pressure pump according to any one of claims 1 to 5, wherein   The said guide | induction means is a spiral member (96) provided in the inside of the said pump cover, and the radial direction of the said pressurization chamber formation member, The Claim 1 characterized by the above-mentioned. The high-pressure pump described.

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