JP2016200013A - Valve device, and fuel pump using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve device which can certainly lower the pressure of a fluid when opening valve, while enhancing open-valve pressure.SOLUTION: A relief valve 40 provided on a fuel pump has a cylinder portion 41 which has a communication path 410 for communicating the inside and outside of a fuel pump, a passage inner wall 412 forming the communication path 410, and a valve seat formed in the passage inner wall 412; a valve member 42 which can abut on the valve seat; a coil spring which energizes the valve member 42 to the valve seat side; and a plurality of guide ribs 45, 46, 47, and 48 which are provided on the passage inner wall 412 of the cylinder portion 41, and guide expanding/contracting movement of the coil spring. A projection height L45 of the guide rib 45 from the passage inner wall 412 is small as compared with projection heights L46, L47, and L48 of the guide ribs 46, 47, and 48 from the passage inner wall 412.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a valve device and a fuel pump using the valve device.

  Conventionally, it is provided between a high-pressure fluid passage through which high-pressure fluid flows and a low-pressure fluid passage through which low-pressure fluid flows. When the pressure of the fluid flowing through the high-pressure fluid passage exceeds a predetermined pressure, the valve is opened. A valve device that allows the flow of fluid to the low-pressure side fluid passage is known. For example, Patent Document 1 discloses an impeller that pressurizes fuel in a fuel tank, a motor that rotates the impeller, a pump housing that houses the impeller and the motor, and a valve that opens when the fuel pressure in the pump housing exceeds a predetermined pressure. A fuel pump is described that includes a relief valve that discharges high pressure fuel in the pump housing to the outside of the pump housing.

JP 2013-253492 A

  The relief valve included in the fuel pump described in Patent Document 1 is formed of a valve housing having a valve seat, a valve member that can contact or separate from the valve seat, and a compression spring that biases the valve member toward the valve seat. ing. In the relief valve having such a configuration, the valve opening pressure, that is, the valve opening pressure is determined by the biasing force of the compression spring. In recent years, with the increase in the pressure of fuel supplied to the engine, the relief valve provided in the fuel pump is set to increase the biasing force of the compression spring and increase the valve opening pressure. However, if the urging force of the compression spring is increased, the fuel pressure in the pump housing after the fuel in the pump housing is released to a certain extent by opening the valve and the valve is closed also increases. For this reason, since the pressure of the fuel in a pump housing cannot fully be reduced, there exists a possibility that the supply pipe | tube connected to a fuel pump, etc. may be damaged with the fuel which a fuel pump discharges.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a valve device that can reliably reduce the pressure of a fluid when the valve is opened while increasing the valve opening pressure. is there.

The present invention includes a valve housing, a valve member, a biasing member, and a plurality of guide portions.
The valve housing has a communication path that allows one side to communicate with the other side, a passage inner wall that forms the communication path, and a valve seat that is formed on the passage inner wall.
The valve member is provided so as to be able to reciprocate in the communication path, and when it comes into contact with the valve seat, the one side and the other side of the valve housing are blocked and the flow of fluid from the other side to the one side is restricted, When separated from the valve seat, the one side and the other side of the valve housing are communicated to allow fluid flow from one side to the other side.
The urging member is provided in the communication path and urges the valve member toward the valve seat.
The guide portion protrudes radially inward from the inner wall of the passage, extends from one side of the valve housing to the other side, and is arranged so as to be arranged at intervals in the circumferential direction of the inner wall of the passage. It is possible to guide the expansion and contraction movement of the urging member.
In the valve device of the present invention, the plurality of guide portions have a normal guide portion whose protrusion height from the inner wall of the passage is a predetermined value, and the protrusion height from the inner wall of the passage is smaller than the protrusion height of the normal guide portion from the inner wall of the passage. And a specific guide part.

  In the valve device of the present invention, when the valve member moves away from the valve seat against the urging force of the urging member, the urging member contracts while being biased toward the specific guide portion side. As a result, the valve member is separated from the valve seat while being eccentric with respect to the central axis of the urging member, so that the lift amount of the valve member is relatively large and a relatively large flow rate from one side to the other side. Of fluids. Therefore, the valve device of the present invention has a relatively large lift amount when the valve is opened even when the valve opening pressure is set high by increasing the biasing force of the biasing member. A relatively large amount of fluid can flow to the other side, and the pressure of the fluid on one side can be reliably reduced.

It is sectional drawing of a fuel pump provided with the valve apparatus by 1st embodiment of this invention. It is the II-II sectional view taken on the line of FIG. It is the III section enlarged view of FIG. It is the IV-IV sectional view taken on the line of FIG. (A) The figure which shows a state when a biasing member is compressed in the valve apparatus by 1st embodiment of this invention, (b) The figure which shows a state when a biasing member is compressed in the valve apparatus of a comparative example It is. It is sectional drawing of the valve apparatus by 2nd embodiment of this invention. It is sectional drawing of the valve apparatus by 3rd embodiment of this invention. It is sectional drawing of the valve apparatus by 4th embodiment of this invention. It is sectional drawing of the valve apparatus by 5th embodiment of this invention. It is sectional drawing of the valve apparatus by other embodiment of this invention. It is sectional drawing of the valve apparatus by other embodiment of this invention.

  A plurality of embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
A fuel pump including a valve device according to a first embodiment of the present invention will be described with reference to FIGS.
The fuel pump 1 sucks fuel in a fuel tank (not shown) and discharges it to an internal combustion engine as a fuel supply target. As shown in FIGS. 1 and 2, the fuel pump 1 includes a housing 10, a pump cover 15, a cover end 25, a stator 30, a rotor 35, a shaft 36, an impeller 37, a relief valve 40 as a “valve device”, and the like. I have. The housing 10, the pump cover 15 and the cover end 25 correspond to a “pump case” described in the claims.

The housing 10 is formed in a cylindrical shape from a metal such as iron.
The pump cover 15 is formed in a substantially disc shape by a metal such as aluminum, for example. The pump cover 15 closes one end of the housing 10. The pump cover 15 is fixed on the inner side of the housing 10 by caulking one end of the housing 10 to the inner side in the radial direction, and is prevented from coming off in the axial direction. As shown in FIG. 1, the pump cover 15 has a cylindrical suction portion 16. The suction part 16 has a suction passage 161 that penetrates the pump cover 15 in the plate thickness direction.

  The cover end 25 is formed in a disk shape with resin, for example. The cover end 25 closes the other end of the housing 10. The cover end 25 is fixed inside the housing 10 by the other end of the housing 10 being caulked inward in the radial direction, and is prevented from coming off in the axial direction.

  In the center of the end surface of the cover end 25 on the pump cover 15 side, a recess 251 is formed that is recessed toward the opposite side of the rotor 35. A cylindrical portion 252 that protrudes in a cylindrical shape on the rotor 35 side is formed at the center of the concave portion 251. A bearing member 26 that is formed in a cylindrical shape from, for example, a copper-based sintered metal is fitted inside the cylindrical portion 252. The bearing member 26 supports one end of the shaft 36.

  A discharge portion 27 is provided on an end surface 253 of the cover end 25 opposite to the pump cover 15. The discharge part 27 is formed integrally with the cover end 25 so as to protrude in a cylindrical shape from the end surface 253. The discharge unit 27 has a discharge passage 271. The discharge passage 271 communicates with the space 11 between the pump cover 15 and the cover end 25 in the housing 10. As shown in FIG. 1, one end of a supply pipe 2 connected to a fuel supply target (not shown), for example, an internal combustion engine, is connected to the discharge unit 27. Thereby, the fuel in the space 11 is supplied to the fuel supply target via the discharge passage 271.

  A plurality of terminals 28 are provided on the end surface 253 of the cover end 25. The terminal 28 is formed in a long plate shape with metal, and one end thereof is electrically connected to the stator 30. In the first embodiment, three terminals 28 are provided, and one end of each terminal 28 is electrically connected to a winding 33 described later. A wire harness (not shown) is connected to the other end of the terminal 28. Electric power is supplied to the winding 33 via the wire harness.

The stator 30 includes a core 31, an insulator 32, a winding 33, and the like. The stator 30 is formed in a substantially cylindrical shape by resin-molding the core 31, the insulator 32, and the winding 33 with resin forming the cover end 25. That is, the stator 30 is formed integrally with the cover end 25. The stator 30 is accommodated inside the housing 10 coaxially with the housing 10.
The core 31 is formed from a laminated iron core in which thin plates of magnetic material are laminated. The core 31 is covered with a resin or an insulator 32 except for a surface facing the central axis of the stator 30.
The insulator 32 is formed in a cylindrical shape and is fitted on the outer periphery of the core 31.
The winding 33 is wound around the outer periphery of the insulator 32. A plurality of sets of cores 31, insulators 32, and windings 33 are provided inside the housing 10 so as to be aligned in the circumferential direction of the housing 10. In the first embodiment, six sets are provided at equal intervals in the circumferential direction of the housing 10. Two windings 33 constitute one phase, and each corresponds to the U phase, the V phase, and the W phase. That is, the stator 30 and the rotor 35 described later constitute a three-phase brushless motor.

  The rotor 35 is formed in a cylindrical shape from a magnetic material. The rotor 35 is provided inside the stator 30 in the radial direction. The rotor 35 is magnetized so that N poles and S poles alternate in the circumferential direction. The rotor 35 has a shaft hole 351 on the central axis. A shaft 36 formed in a rod shape with metal is press-fitted and fixed in the shaft hole 351. As a result, the shaft 36 can rotate together with the rotor 35.

  A pump casing 17 is provided between the stator 30 and the rotor 35 and the pump cover 15. The pump casing 17 is formed in a substantially disk shape from a metal such as aluminum, for example. The pump casing 17 has a through-hole 171 passing through the pump casing 17 in the thickness direction at the center. For example, a bearing member 18 that is formed in a cylindrical shape from a copper-based sintered metal is fitted into the through-hole 171. The bearing member 18 supports the other end of the shaft 36.

  The impeller 37 is formed in a substantially disk shape from resin. The impeller 37 is accommodated in a substantially disc-shaped pump chamber 19 formed between the pump cover 15 and the pump casing 17. One end of the shaft 36 is provided so that a part of the outer wall is chamfered in a planar shape and is located in the pump chamber 19. A fitting hole 371 having a shape corresponding to the shape of one end of the shaft 36 is formed at the center of the impeller 37. One end of the shaft 36 is fitted in the fitting hole 371 of the impeller 37. Thus, when the shaft 36 rotates, the impeller 37 rotates in the pump chamber 19.

  A substantially C-shaped groove 151 is formed on the surface of the pump cover 15 on the impeller 37 side. The groove 151 communicates with the suction passage 161. A substantially C-shaped groove 172 is formed on the surface of the pump casing 17 on the impeller 37 side. The groove 172 communicates with a passage 173 that penetrates the pump casing 17 in the plate thickness direction. A groove 372 is formed in the impeller 37 at a position corresponding to the groove 151 and the groove 172.

  As shown in FIGS. 3 and 4, the relief valve 40 includes a cylinder portion 41 as a “valve housing”, a valve member 42, a coil spring 43 as an “urging member”, a locking member 44, and a “guide portion”. It has four guide ribs 45, 46, 47, 48 and the like. The relief valve 40 is provided on the cover end 25. When the pressure of the fuel in the space 11 in the housing 10 exceeds a predetermined pressure, the relief valve 40 separates the valve member 42 from the valve seat 411 and discharges the fuel in the space 11 to the outside of the housing 10. 11 pressure can be reduced.

  The cylinder portion 41 is provided on the cover end 25 so as to protrude from the end surface 253 of the cover end 25. The cylinder portion 41 has a communication path 410 that allows the space 11 to communicate with the outside of the housing 10. As shown in FIG. 4, the passage inner wall 412 of the cylindrical portion 41 that forms the communication passage 410 is formed so that the cross-sectional shape is a circular shape centering on the central axis CA <b> 41 of the cylindrical portion 41. The communication path 410 is formed such that the inner diameter on the cover end 25 side is smaller than the inner diameter on the side opposite to the cover end 25. The inner wall on the cover end 25 side has a tapered valve seat 411. The center of the valve seat 411 is located on the central axis CA41.

  The valve member 42 is formed, for example, in a spherical shape, and is provided so as to be able to reciprocate in the communication path 410. The valve member 42 can contact the valve seat 411 or be separated from the valve seat 411. When the valve member 42 comes into contact with the valve seat 411, the space 11 and the outside of the housing 10 are blocked, and the flow of fluid from the outside of the housing 10 to the space 11 is restricted. Further, when the valve member 42 is separated from the valve seat 411, the space 11 communicates with the outside of the housing 10 via the communication passage 410, and fuel flow from the space 11 to the outside of the housing 10 is permitted.

  The coil spring 43 is a so-called compression spring and is provided so that one end thereof is in contact with the valve member 42. The other end is locked to a locking member 44 provided on the inner side opposite to the end surface 253 of the cylindrical portion 41. The coil spring 43 biases the valve member 42 toward the valve seat 411 side. When there is no fuel in the space 11, the valve member 42 is in contact with the valve seat 411 by the biasing force of the coil spring 43.

As shown in FIG. 4, the guide ribs 45, 46, 47, 48 are provided at equal intervals in the circumferential direction of the passage inner wall 412. The guide ribs 45, 46, 47, 48 are formed so as to protrude radially inward from the passage inner wall 412 and extend from the cover end 25 side of the cylindrical portion 41 to the locking member 44 side. The guide ribs 45, 46, 47, 48 are formed so that the cross-sectional shape perpendicular to the central axis CA41 is an arc.
The guide ribs 45, 46, 47, 48 have inner walls 451, 461, 471, 481 on the radially inner side. The inner walls 451, 461, 471, 481 are formed along the virtual cylindrical surface VL40 centering on the central axis CA41. The inner walls 451, 461, 471, 481 can abut on the radially outer side of the coil spring 43 (virtual surface VL 43 shown in FIG. 4). The guide ribs 45, 46, 47 and 48 guide the expansion and contraction movement of the coil spring 43.

  Of the guide ribs 45, 46, 47, 48, the guide rib 45 as the “specific guide part” has a protrusion height L 45 from the passage inner wall 412 that is higher than the guide inner wall 412 of the guide ribs 46, 47, 48 as the “normal guide part”. The protrusion heights L46, L47, and L48 are smaller than the protrusion height L46.

  In the fuel pump 1, when electric power is supplied to the winding 33 via the terminal 28, the impeller 37 rotates together with the rotor 35 and the shaft 36. When the impeller 37 rotates, the fuel in the fuel tank that houses the fuel pump 1 is guided to the groove 372 via the suction passage 161. The fuel guided to the groove 372 is pressurized by the rotation of the impeller 37. The pressurized fuel passes through the passage 173 and is guided to the space 11. The fuel guided to the space 11 is supplied to the supply pipe 2 through the discharge passage 271. The relief valve 40 is opened when the pressure of the fuel in the space 11 exceeds a predetermined pressure, and prevents the fuel pump 1 or the supply pipe 2 from being damaged by the high pressure fuel.

Next, the effect of the relief valve 40 of the first embodiment will be described in comparison with the relief valve of the comparative example.
FIG. 5A shows a sectional view of the relief valve 40 according to the first embodiment. FIG. 5B shows a sectional view of a relief valve 90 of a comparative example. FIG. 5 shows a state where the same force is applied in the valve opening direction to the valve member 42 of the relief valve 40 and the valve member 92 of the relief valve 90. In FIG. 5, the position of the valve member when the valve is closed is indicated by dotted lines 42 and 92.
The relief valve 90 of the comparative example includes a cylindrical portion 91 having the same shape as the cylindrical portion 41, a valve member 92 having the same shape as the valve member 42, a coil spring 93 having the same urging force as the coil spring 43, guide ribs 95 and 97, and the like. . In the relief valve 90, the guide ribs 95 and 97 provided on the passage inner wall 912 of the cylindrical portion 91 are formed so that the protruding heights L95 and L97 from the passage inner wall 912 have the same size. The relief valve 90 of the comparative example has four guide ribs as in the first embodiment, and these four guide ribs are formed so that the protruding height from the passage inner wall 912 has the same size. ing.

When the valve member 42 is separated from the valve seat 411 in the relief valve 40 according to the first embodiment, the coil spring 43 is compressed. At this time, as shown in FIG. 5A, the coil spring 43 contracts while being biased toward the guide rib 45 having a relatively small protrusion height L45. Accordingly, the valve member 42 is separated from the valve seat 411 while being eccentric with respect to the central axis CA41, and thus the lift amount of the valve member 42 is the lift amount L40.
On the other hand, when the valve member 92 is separated from the valve seat 911 and the coil spring 93 is compressed in the relief valve 90 of the comparative example, the coil spring 93 is deformed radially outward by the four guide ribs such as the guide ribs 95 and 97. Therefore, the coil spring 93 contracts in the direction of the central axis CA91 of the cylindrical portion 91 without being biased in the radially outward direction. For this reason, since the valve member 92 is separated from the valve seat 911 without being eccentric with respect to the central axis CA91, the lift amount of the valve member 92 becomes a lift amount L90 smaller than the lift amount L40 of the relief valve 40. .

  As described above, in the relief valve 40 according to the first embodiment, the protruding height L45 of the guide rib 45 is made smaller than the protruding heights L46, L47, and L48 of the guide ribs 46, 47, and 48, so that the coil spring is opened. 43 contracts while being biased toward the guide rib 45. When the coil spring 43 contracts while being biased toward the guide rib 45, the valve member 42 is separated from the valve seat 411 while being eccentric with respect to the central axis CA41, and the lift amount of the valve member 42 is increased. When the lift amount of the valve member 42 increases, the amount of fuel that can be discharged to the outside of the fuel pump 1 by opening the valve once increases. Thereby, even if the opening pressure of the relief valve 40 is increased by increasing the biasing force of the coil spring 43, once the valve is opened, the fuel pressure in the space 11 can be reliably reduced. Therefore, the fuel pump 1 according to the first embodiment sets the fuel that can be supplied to the engine at a relatively high pressure, and when the fuel pressure in the housing 10 exceeds a predetermined pressure, the relief valve 40 causes the housing 10 to The internal pressure can be reliably reduced to prevent the fuel pump 1 and the supply pipe 2 from being damaged.

(Second embodiment)
Next, a valve device according to a second embodiment of the present invention will be described with reference to FIG. The second embodiment differs from the first embodiment in the shape of the guide rib. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  FIG. 6 shows a sectional view of a relief valve 50 as a “valve device” according to the second embodiment. The relief valve 50 includes a cylindrical portion 41, a valve member 42, a coil spring 43, a locking member 44, four guide ribs 55, 56, 57, 58 as “guide portions”. The relief valve 50 is provided on the end surface 253 of the cover end 25.

  The guide ribs 55, 56, 57 and 58 are provided at equal intervals in the circumferential direction of the passage inner wall 412. The guide ribs 55, 56, 57, 58 are formed so as to protrude in the radial inward direction from the passage inner wall 412. The guide ribs 55, 56, 57, 58 have inner walls 551, 561, 571, 581 on the radially inner side. The inner walls 551, 561, 571, 581 are formed along the virtual cylindrical surface VL40 centering on the central axis CA41. The inner walls 551, 561, 571, 581 are formed so as to be able to contact the radially outer side of the coil spring 43. The guide ribs 55, 56, 57 and 58 guide the expansion and contraction movement of the coil spring 43.

  Of the guide ribs 55, 56, 57, 58, the guide ribs 55, 56 as “specific guide portions” are the passage inner walls of the guide ribs 57, 58 whose projection heights L 55, L 56 from the passage inner wall 412 are “normal guide portions”. The protrusion heights L57 and L58 from 412 are formed to be smaller.

In the second embodiment, when the valve is closed, the coil spring 43 contracts while being biased toward the guide ribs 55 and 56 having relatively small protrusion heights L55 and L56. Thereby, since the valve member 42 is separated from the valve seat 411 while being eccentric with respect to the central axis CA41, the lift amount of the valve member 42 can be increased. Therefore, the second embodiment has the same effect as the first embodiment.
In the second embodiment, the guide ribs 55 and 56 are provided at adjacent positions. As a result, the coil spring 43 is more likely to be biased toward the side where the guide ribs 55 and 56 are provided. Therefore, the lift amount of the valve member 42 can be further increased.

(Third embodiment)
Next, a valve device according to a third embodiment of the present invention will be described with reference to FIG. The third embodiment is different from the first embodiment in the shape of the guide rib. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  FIG. 7 shows a sectional view of a relief valve 60 as a “valve device” according to a third embodiment. The relief valve 60 includes a cylindrical portion 41, a valve member 42, a coil spring 43, a locking member 44, four guide ribs 65, 66, 67, 68 as “guide portions”. The relief valve 60 is provided on the end surface 253 of the cover end 25.

  The guide ribs 65, 66, 67 and 68 are provided at equal intervals in the circumferential direction of the passage inner wall 412. The guide ribs 65, 66, 67, 68 are formed so as to protrude inward from the passage inner wall 412. The guide ribs 65, 66, 67, 68 have inner walls 651, 661, 671, 681 on the radially inner side. The inner walls 651, 661, 671, 681 are formed along the virtual cylindrical surface VL40 centering on the central axis CA41. The inner walls 651, 661, 671, 681 are formed so as to be able to contact the outer side in the radial direction of the coil spring 43. The guide ribs 65, 66, 67 and 68 guide the expansion and contraction motion of the coil spring 43.

  Of the guide ribs 65, 66, 67, 68, the guide ribs 65, 66, 67 serving as “specific guide portions” have protrusion heights L 65, L 66, L 67 from the passage inner wall 412 of the guide rib 68 serving as “normal guide portions”. It is formed to be smaller than the projection height L68 from the passage inner wall 412.

In the third embodiment, when the valve is closed, the coil spring 43 contracts while being biased toward the guide ribs 65, 66, and 67 having relatively small protrusion heights L65, L66, and L67. Thereby, since the valve member 42 is separated from the valve seat 411 while being eccentric with respect to the central axis CA41, the lift amount of the valve member 42 can be increased. Therefore, the third embodiment has the same effect as the first embodiment.
In the third embodiment, the guide ribs 65, 66, and 67 are provided at adjacent positions. As a result, the coil spring 43 is more likely to be biased toward the side where the guide ribs 65, 66 and 67 are provided. Therefore, the lift amount of the valve member 42 can be further increased.

(Fourth embodiment)
Next, a valve device according to a fourth embodiment of the present invention will be described with reference to FIG. The fourth embodiment differs from the first embodiment in the number of guide ribs. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  A sectional view of a relief valve 70 as a “valve device” according to a fourth embodiment is shown in FIG. The relief valve 70 includes a cylindrical portion 41, a valve member 42, a coil spring 43, a locking member 44, three guide ribs 75, 76, 77 as “guide portions”. The relief valve 70 is provided on the end surface 253 of the cover end 25.

  The guide ribs 75, 76, 77 are provided at equal intervals in the circumferential direction of the passage inner wall 412. The guide ribs 75, 76, 77 are formed so as to protrude from the passage inner wall 412 in the radially inward direction. The guide ribs 75, 76, 77 have inner walls 751, 761, 771 on the radially inner side. The inner walls 751, 761, 771 are formed along a virtual cylindrical surface VL40 centered on the central axis CA41. The inner walls 751, 761, 771 are formed so as to be able to contact the radially outer side of the coil spring 43. The guide ribs 75, 76 and 77 guide the expansion and contraction movement of the coil spring 43.

  Of the guide ribs 75, 76, 77, the guide rib 75 serving as the “specific guide portion” has a protruding height L 75 from the passage inner wall 412 that is a height protruding from the passage inner wall 412 of the guide rib 76, 77 as the “normal guide portion”. It is formed to be smaller than L76 and L77.

  In the fourth embodiment, when the valve is closed, the coil spring 43 contracts while being biased toward the guide rib 75 having a relatively small protrusion height L75. Thereby, since the valve member 42 is separated from the valve seat 411 while being eccentric with respect to the central axis CA41, the lift amount of the valve member 42 can be increased. Therefore, the fourth embodiment has the same effect as the first embodiment.

(Fifth embodiment)
Next, a valve device according to a fifth embodiment of the present invention will be described with reference to FIG. The fifth embodiment is different from the fourth embodiment in the shape of the guide rib. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 4th embodiment, and description is abbreviate | omitted.

  FIG. 9 shows a sectional view of a relief valve 80 as a “valve device” according to a fifth embodiment. The relief valve 80 includes a cylindrical portion 41, a valve member 42, a coil spring 43, a locking member 44, three guide ribs 85, 86, 87 as “guide portions”. The relief valve 80 is provided on the end surface 253 of the cover end 25.

  The guide ribs 85, 86 and 87 are provided at equal intervals in the circumferential direction of the passage inner wall 412. The guide ribs 85, 86, 87 are formed so as to protrude from the passage inner wall 412 in the radially inward direction. The guide ribs 85, 86, 87 have inner walls 851, 861, 871 on the radially inner side. The inner walls 851, 861, and 871 are formed along the virtual cylindrical surface VL40 with the central axis CA41 as the center. The inner walls 851, 861, 871 are formed so as to be able to abut on the radially outer side of the coil spring 43. The guide ribs 85, 86 and 87 guide the expansion and contraction movement of the coil spring 43.

  Of the guide ribs 85, 86, 87, the guide ribs 85, 86 as “specific guide portions” protrude from the passage inner wall 412 of the guide ribs 87 having protrusion heights L 85, L 86 from the passage inner wall 412 as “normal guide portions”. It is formed to be shorter than the height L87.

In the fifth embodiment, when the valve is closed, the coil spring 43 contracts while being biased toward the guide ribs 85 and 86 having relatively small protrusion heights L85 and L86. Thereby, since the valve member 42 is separated from the valve seat 411 while being eccentric with respect to the central axis CA41, the lift amount of the valve member 42 can be increased. Therefore, the fifth embodiment has the same effect as the first embodiment.
In the fifth embodiment, the guide ribs 85 and 86 are provided at adjacent positions. As a result, the coil spring 43 is more likely to be biased toward the side where the guide ribs 85 and 86 are provided. Therefore, the lift amount of the valve member 42 can be further increased.

(Other embodiments)
In the above-described embodiment, the “valve device” of the present invention is used as a relief valve. However, the “valve device” is not limited to the relief valve. Any valve device having a biasing member that biases the valve member may be used.

  In the above-described embodiment, the passage inner wall of the cylindrical portion as the “valve housing” is formed so that the cross-sectional shape is a circular shape centering on the central axis of the cylindrical portion. The center of the valve seat is assumed to be located on the central axis of the cylindrical portion. However, the cross-sectional shape of the inner wall of the valve housing and the position of the center of the valve seat are not limited to this.

  In the above-described embodiment, the guide rib is formed so that the cross-sectional shape perpendicular to the central axis is an arc shape. In addition, the inner wall of the guide rib is formed so as to be along a virtual cylindrical surface centered on the central axis. However, the shape of the guide rib is not limited to this. For example, like the guide ribs 491, 492, 493, and 494 provided in the relief valve 49 shown in FIG. 10, the cross-sectional shape perpendicular to the central axis CA41 may be formed in a substantially triangular shape. Further, like the guide ribs 591, 592, 593, 594 provided in the relief valve 59 shown in FIG. 11, the cross-sectional shape perpendicular to the central axis CA 41 may be formed into an arc shape protruding in the radial direction.

  In the second, third, and fifth embodiments, the specific guide portion is provided so as to be adjacent in the circumferential direction. However, the specific guide portions do not have to be adjacent to each other.

  In the above-described embodiment, the relief valve is provided with the coil spring as the “biasing member”. However, the kind of urging member is not limited to this.

  In the above-described embodiment, the relief valve includes a spherical valve member, and the valve seat is formed in a tapered shape. However, the shape of the valve member and the shape of the valve seat are not limited to this.

  In the above-described embodiment, the number of guide ribs is three or four. However, the number of guide ribs is not limited to this. The number of guide ribs may be two, or five or more.

  In the above-described embodiment, the guide ribs are provided at equal intervals in the circumferential direction of the inner wall of the cylindrical portion. However, the position where the guide rib is provided is not limited to this.

  Thus, the present invention is not limited to the above-described embodiment, and can be implemented in various forms without departing from the gist thereof.

40, 49, 50, 59, 60, 70, 80 ... relief valve (valve device)
41 ..Cylinder part (valve housing)
42 ... Valve member 43 ... Coil spring (biasing member)
45, 491, 55, 56, 591, 65, 66, 67, 75, 85, 86 ... guide ribs (specific guide portions)
46, 47, 48, 492, 493, 494, 57, 58, 592, 593, 594, 68, 76, 77, 87 ... guide ribs (normal guide portions)
410 ... Communication path 411 ... Valve seat 412 ... Inner wall 451, 461, 471, 481, 551, 561, 571, 581, 651, 661, 671, 681, 751, 761, 771, 851, 861 , 871 ... inner wall

Claims (10)

A valve housing (41) having a communication passage (410) capable of communicating with one side and the other side, a passage inner wall (412) forming the communication passage, and a valve seat (411) formed on the passage inner wall. )When,
Provided in the communication passage so as to be capable of reciprocating, and when abutting against the valve seat, the one side and the other side of the valve housing are cut off to restrict the flow of fluid from the other side to the one side, A valve member (42) that communicates between one side and the other side of the valve housing when separated from the valve seat and allows fluid to flow from one side to the other;
A biasing member (43) provided in the communication path and biasing the valve member toward the valve seat;
The diameter of the biasing member is provided so as to protrude radially inward from the inner wall of the passage and to extend from one side of the valve housing to the other side, and to be arranged at intervals in the circumferential direction of the inner wall of the passage. A plurality of guide portions (45, 46, 47, 48, 491, 492, 493, 494, 55, 56, 57 that are formed so as to be able to contact the outer side (VL43) in the direction and can guide the expansion and contraction movement of the biasing member. 58, 591, 592, 593, 594, 65, 66, 67, 68, 75, 76, 77, 85, 86, 87),
With
The plurality of guide portions are normal guide portions (46, 47, 48, 492, 493, 494, 57, 58, 592, 593, 594, 68, 76, the protrusion height from the inner wall of the passage is a predetermined value. 77, 87), and specific guide portions (45, 491, 55, 56, 591, 65, 66, 67, the protrusion height from the inner wall of the passage is smaller than the protrusion height of the normal guide portion from the inner wall of the passage, 75, 85, 86).   The valve device according to claim 1, wherein the biasing member is a coil spring. The valve member is formed in a spherical shape,
The valve device according to claim 1 or 2, wherein the valve seat is formed in a tapered shape.   The valve device according to any one of claims 1 to 3, wherein a plurality of the specific guide portions are provided so as to be adjacent to each other in a circumferential direction of the inner wall of the passage. The passage inner wall is formed so that a cross-sectional shape perpendicular to the central axis (CA41) is circular,
The valve device according to any one of claims 1 to 4, wherein the valve seat is formed so that a center is located on the central axis.   The valve device according to claim 5, wherein the guide portion is formed so that a cross-sectional shape perpendicular to the central axis is an arc shape.   The guide portion is formed along a virtual cylindrical surface (VL40) centered on the central axis, and wall surfaces (451, 461, 471, 481, 551, 561, 571, 581, which can contact the biasing member). 651, 661, 671, 681, 751, 761, 771, 851, 861, 871).   The valve device according to any one of claims 1 to 7, wherein the plurality of guide portions are provided so as to be arranged at equal intervals in a circumferential direction of the inner wall of the passage.   The valve device according to any one of claims 1 to 8, comprising three guide portions. A pump case (10, 15, 25) having a suction passage (161) for sucking fuel and a discharge passage (271) for discharging fuel;
A plurality of windings (33) wound around, a cylindrical stator (30) accommodated inside the pump case;
A rotor (35) rotatably provided on the radially inner side of the stator;
A shaft (36) provided coaxially with the rotor and rotating integrally with the rotor;
An impeller (37) having a fitting hole (371) into which one end of the shaft is fitted, pressurizing fuel sucked from the suction passage and discharging from the discharge passage when rotating together with the shaft;
One side of the valve housing is connected to the pump case, and the communication path is provided to communicate with the inside of the pump case, allowing fuel flow from the inside of the pump case to the outside of the pump case, The valve device according to any one of claims 1 to 9, which regulates the flow of fuel from the outside of the pump case to the inside of the pump case.
A fuel pump comprising:

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