JP6921666B2 - Pressure controller and fuel supply - Google Patents

Description

The present invention relates to a pressure control device and a fuel supply device.

Conventionally, for example, vehicles such as motorcycles and four-wheeled vehicles are provided with a fuel supply device for pumping fuel, which is a fluid, to an internal combustion engine which is a supply destination. Some fuel supply devices are equipped with a pressure control device. The pressure control device controls the pressure of the fuel pumped from the fuel supply device to prevent the fuel pressure from becoming excessive.

As the pressure control device, for example, there is a pressure control device disclosed in Patent Document 1. The pressure control device of Patent Document 1 includes a case, a valve, a pressed portion, and a driving portion. Inside the case, a gangway is provided so as to penetrate in the axial direction of the case. The valve closes the closed portion set in the gangway so that it can be opened and closed. The pressed portion is provided on the other side in the axial direction of the valve. The pressed portion is fitted to the valve. The drive unit is arranged in the gangway in a state where the pressed portion is pressed with a predetermined pressure from the other side in the axial direction of the pressed portion.

When the pressure of the fuel stored on one side in the axial direction from the closed part of the gangway exceeds a predetermined pressure, the drive part moves the pressed part and the valve to the other side in the axial direction to move the closed part. Open. As a result, the fuel flows to the other side in the axial direction of the gangway. This lowers the fuel pressure. As a result, the pressure of the fuel pumped from the fuel supply device to the internal combustion engine also decreases, and the fuel pressure is prevented from becoming excessive.

Japanese Unexamined Patent Publication No. 2016-183599

However, in the pressure control device of Patent Document 1, since the valve and the pressed portion are simply fitted, the assembling force between the valve and the pressed portion is not sufficient. Therefore, even if the valve and the pressed portion are assembled in the manufacture of the pressure control device, the valve and the pressed portion may come off, for example, when other parts are assembled. In that case, the valve and the pressed portion will be reassembled, and the assembling work will take time. Therefore, the manufacturing efficiency of the pressure control device is not good.

Therefore, it is conceivable to assemble the valve and the pressed portion using an adhesive, but it takes time to assemble because the adhesive application work is required. Therefore, in this case as well, the manufacturing efficiency of the pressure control device is not good. Further, when the valve swells, the shape of the entire valve becomes large, so that the gangway blockage becomes higher than usual. As a result, even if the fuel pressure exceeds a predetermined pressure, the valve cannot sufficiently move to the other side, and it takes time for the fuel stored in the gangway to flow out, so that it takes time to reduce the fuel pressure. Therefore, in the pressure control device in this case, the fuel pressure control function is deteriorated.

The present invention has been made in view of such conventional problems, and pressure control can improve manufacturing efficiency and suppress a decrease in the pressure control function of the fluid even if the valve swells. It is an object of the present invention to provide an apparatus and a fuel supply apparatus.

The pressure control device of the present invention closes the case, the through-passage provided through the inside of the case along the axial direction, and the closed portion set in the through-passage so as to be openable and closable. The through path in a state where the valve, the pressed portion provided on the other side of the valve in the axial direction, and the pressed portion of the pressed portion from the other side in the axial direction are pressed with a predetermined pressure. When the pressure of the fluid stored in one side of the through-passage in the axial direction exceeds the predetermined pressure, the pressed portion and the valve are placed on the other side in the axial direction. A pressure control device including a drive unit that is moved to the valve to open the closed portion, and a plurality of first press-fitting portions and a center in the axial plan view on the other side surface of the valve in the axial direction. A plurality of second press-fitting portions recessed on the side are provided alternately in the circumferential direction and are formed by being connected in an annular shape , and the plurality of second press-fitting portions are formed on one side surface of the pressed portion in the axial direction. 1 press-fit portion, characterized in that the press-fitted portion that is press-fitted is provided.

In the pressure control device of the present invention, since the valve and the pressed portion are fitted by press fitting, a sufficient assembling force between the valve and the pressed portion is secured. Therefore, no adhesive is required for assembling the valve and the pressed portion, so that the work of applying the adhesive is not required. Therefore, it is possible to shorten the time required for assembling the valve and the pressed portion in the manufacture of the pressure control device. Therefore, the pressure control device of the present invention can increase the manufacturing efficiency.

In the pressure control device of the present invention, since the second press-fitting portion is press-fitted more loosely with respect to the press-fitting portion than the first press-fitting portion, when the valve swells, the swelling portion is transferred between the second press-fitting portion and the press-fitted portion. It becomes possible to tolerate between. Therefore, even if the valve swells, it is suppressed that the shape of the entire valve becomes large, so that the gangway blocking property is suppressed from becoming higher than usual. As a result, even if the pressure of the fluid exceeds a predetermined pressure, the valve sufficiently moves to the other side, so that it is possible to prevent the fluid stored in the gangway from taking a long time to flow out. Therefore, it is suppressed that it takes time to reduce the pressure of the fluid. Therefore, the pressure control device of the present invention can suppress a decrease in the pressure control function of the fluid even if the valve swells.

In the pressure control device of the present invention, it is desirable that at least three of the plurality of first press-fitting portions and the plurality of second press-fitting portions are arranged at equal intervals in the circumferential direction.

As a result, when the valve swells, the swelling amount can be allowed between the second press-fitted portion and the press-fitted portion over the entire circumference of the valve. Therefore, even if the valve swells, it is further suppressed that the shape of the entire valve becomes large, so that the obstruction of the gangway becomes higher than usual. As a result, even if the pressure of the fluid exceeds a predetermined pressure, the valve moves more sufficiently to the other side, so that it is further suppressed that the fluid stored in the gangway takes a long time to flow out, and the pressure of the fluid is lowered. It is further suppressed that it takes time. Therefore, the pressure control device of the present invention can further suppress a decrease in the pressure control function of the fluid even if the valve swells.

In the pressure control device of the present invention, the plurality of first press-fitting portions and the plurality of second press-fitting portions are formed so that the cross-sectional shape along the axial direction is convex, and the press-fitting portion is formed. It is desirable that the cross-sectional shape along the axial direction is concave.

As a result, the valve and the pressed portion can be assembled in a shape that is easy to manufacture, so that the cost for assembling can be suppressed. Therefore, the pressure control device of the present invention can reduce the manufacturing cost.

In the pressure control device of the present invention, it is desirable that the plurality of first press-fitting portions and the plurality of second press-fitting portions are formed by being connected in an annular shape in the circumferential direction.

As a result, the plurality of first press-fitting portions and the plurality of second press-fitting portions can be easily press-fitted into the press-fitting portion so that the press-fitting positions can be easily adjusted with respect to the press-fitting portion. It will be possible. Therefore, it is possible to further reduce the time required for assembling the valve and the pressed portion in the manufacture of the pressure control device. Therefore, the pressure control device of the present invention can further improve the manufacturing efficiency.

In the pressure control device of the present invention, the case has a swellability lower than that of the valve, and the valve is formed on the inner peripheral surface on one side of the through-passage in the axial direction with respect to the blocked portion. It is desirable that a locking portion is provided that presses and locks one side surface in the axial direction over the entire circumference.

As a result, even if the valve swells, the locking portion does not swell, so that the pressing state of the locking portion against the valve is maintained. Therefore, the pressure control device of the present invention can prevent a decrease in the blockage of the gangway even if the valve swells.

In the pressure control device of the present invention, it is desirable that a protrusion is provided on one side surface of the valve in the axial direction.

As a result, when the pressure of the fluid is controlled, the fluid stored in the through-passage flows to the outer peripheral side of the valve by hitting the protrusion when flowing out from the through-passage. Therefore, the pressure control device of the present invention can efficiently flow the fluid to the outer peripheral side of the valve as compared with the case where there is no protrusion, so that the pressure of the fluid can be reduced efficiently. Therefore, the pressure control device of the present invention can efficiently control the pressure of the fluid.

The fuel supply device of the present invention is a fuel supply device that pumps fuel as a fluid to a supply destination, and includes a pressure control device that controls the pressure of the fuel pumped to the supply destination, and the pressure control device. Is characterized in that the pressure control device of the present invention is used.

As a result, the fuel supply device of the present invention can increase the manufacturing efficiency of the pressure control device, so that the manufacturing efficiency of the entire fuel supply device can be increased. Further, the fuel supply device of the present invention can suppress a decrease in the pressure control function of the fuel even if the valve of the pressure control device swells.

The pressure control device and the fuel supply device of the present invention can increase the manufacturing efficiency and can suppress a decrease in the pressure control function of the fluid even if the valve swells.

It is a perspective view of the fuel supply device of one Embodiment of this invention. It is sectional drawing along the axial direction of the fuel supply device in embodiment of this invention. It is a perspective view of the pressure regulator of the same embodiment. It is sectional drawing along the axial direction of the pressure regulator of the same embodiment. It is a bottom view of the valve of the same embodiment. It is a perspective view of the pressed portion of the same embodiment as viewed from below. It is a bottom view of the pressed portion of the same embodiment. It is a figure which shows the state which the closed part of the gangway and the radial flow path are open from the state of FIG. It is a bottom view of the valve of another embodiment.

Next, an embodiment of the present invention will be described with reference to the drawings.

FIG. 1 is a perspective view of the fuel supply device 1 according to the embodiment of the present invention. FIG. 2 is a cross-sectional view taken along the axial direction Z of the fuel supply device 1.
In the drawings below, the vertical direction of the fuel supply device 1 is the axial direction Z. Here, one side of the axial direction Z is the upper side, and the other side of the axial direction Z is the lower side. In FIG. 1, the left-right direction of the fuel supply device 1 is the radial direction R. Here, one side of the radial direction R is the left side, and the other side of the radial direction R is the right side. In FIG. 1, the circumferential direction θ of the fuel supply device 1 is as shown in the figure. The same applies to the following figure.

(Fuel supply device)
As shown in FIGS. 1 and 2, the fuel supply device 1 is arranged so as to be immersed in fuel in a fuel tank 2 of, for example, an automobile or a motorcycle, and pumps up the fuel in the fuel tank 2 to provide an internal combustion engine (not shown). It is pumped to the engine.
The fuel supply device 1 includes a fuel pump 3, a holder portion 191 including the fuel pump 3 and attached to the fuel tank 2, and a filter unit 192 arranged on the suction side of the fuel pump 3. Further, a sender gauge 193 is provided on the filter unit 192 side of the holder portion 191.

The fuel pump 3 has a motor unit M arranged on the flange unit 4 side and a pump unit P attached to the lower end of the motor unit M.
The motor unit M is a so-called brushed DC motor. The motor portion M includes a metal tubular motor housing (yoke) 6, an armature 7 rotatably provided inside the motor housing 6, and an outlet cover 8 that closes the upper opening of the motor housing 6. I have. A plurality of permanent magnets 19 are arranged on the inner peripheral surface of the motor housing 6 so that magnetic poles alternate in the circumferential direction.

The armature 7 is provided with an armature core 10 having a predetermined number of poles at the center of the rotating shaft 9, and a commutator 11 is provided on the upper end side of the rotating shaft 9 so as to come into contact with the brush. The armature core 10 is a stack of a plurality of core plates 12 in the axial direction. In the core plate 12, a substantially T-shaped tooth 13 extending radially outward in the radial direction is integrally formed on the outer peripheral surface of the annular portion formed in a substantially annular shape. A slot (not shown) is formed between the adjacent teeth 13, and the winding 15 is wound around the teeth 13 through this slot.

The commutator 11 provided on the upper end side of the rotating shaft 9 is a so-called disc type commitator formed in a substantially disk shape. A plurality of segments 16 are formed on the upper surface of the commutator 11 at equal intervals in the circumferential direction and are insulated from each other. The upper surface of the commutator 11 is a sliding surface of a brush (not shown).
The brush is located above the commutator 11. The brush is urged toward the commutator 11 side by a spring (not shown). The tip of the brush is in sliding contact with the segment 16. Further, the brush is electrically connected to an external power source (not shown) and supplies power to the winding 15 connected to the segment 16 of the commutator 11.

On the other hand, a riser 18 for connecting the winding 15 to the commutator 11 is provided on the lower surface of the commutator 11. The winding 15 is connected to the riser 18 by fusing or the like. Each segment 16 and the riser 18 are electrically connected.

The outlet cover 8 that closes the upper opening of the motor housing 6 is formed of a resin or the like in a substantially columnar shape. At substantially the center of the outlet cover 8 in the axial direction, a skirt portion 21 formed in a divergent manner is provided from the upper portion to the lower portion. The lower end of the skirt portion 21 comes into contact with the motor housing 6, whereby the outlet cover 8 is positioned in the axial direction.

Further, the motor housing 6 crimps the upper end of the motor housing so as to cover the skirt portion 21 of the outlet cover 8 placed on the upper portion of the motor housing 6. As a result, the outlet cover 8, the motor portion M, and the pump portion P are integrally fixed to the motor housing 6. Further, at the lower end of the skirt portion 21, a tongue piece portion 23 protruding in the axial direction is provided on the outer peripheral edge.

A storage recess 24 is formed in the lower center of the outlet cover 8, and a commutator 11 is housed in the storage recess 24. A bearing portion 25 that rotatably supports the rotating shaft 9 is formed in the upper wall 24a of the accommodating recess 24 in the center in the radial direction.
The bearing portion 25 may be any bearing as long as it can radially support the rotating shaft, and various radial sliding bearings can be preferably adopted. In particular, it is preferable to have a material or structure capable of obtaining a lubricating effect by allowing fuel to permeate into the bearing gap. Further, the bearing portion 25 may be fixed to a bearing which is a separate member, or may be formed on the outlet cover 8 itself.

Two recesses 29 (only one is described in the first embodiment) are formed on the upper portion of the outlet cover 8 near the outer periphery, and male terminals 30 are erected in each of the recesses 29. The male terminal 30 is arranged in a direction along the longitudinal direction of the recess 29, and is erected along the axial direction. The base end side of the male terminal 30 is electrically connected to a brush (not shown).

Further, near the outer periphery of the outlet cover 8, a tubular check valve accommodating portion 31 is erected on the opposite side of the rotation shaft 9 from the position where the recess 29 is formed. The check valve accommodating portion 31 is formed so that the tip side is reduced in diameter due to a step. A check valve 32 is built in the check valve storage unit 31. Further, an O-ring 231 used when attaching the outlet cover 8 to the flange unit 4 is provided on the stepped surface 31a formed on the outer peripheral surface of the check valve accommodating portion 31.

A stepped hole is formed below the check valve accommodating portion 31, and this hole is used as a discharge port 33. That is, the outlet cover 8 is formed with a hole that penetrates the discharge port 33 and the check valve accommodating portion 31 in the axial direction. Then, the fuel pumped by the pump unit P is discharged to the outside of the fuel pump 3 (outlet cover 8) through the discharge port 33 and the check valve 32.

The pump portion P is provided so as to close the lower opening of the motor housing 6. The pump portion P includes a base bracket 20 arranged on the upper portion of the pump portion P, an impeller 100 rotatably provided along the lower surface of the base bracket 20, and an inlet cover 38 covering the impeller 100 from below. It is composed of. The pump portion P is sandwiched and fixed in the motor housing 6 by the lower opening edge of the motor housing 6 bent inward and the motor portion M crimped and fixed to the outlet cover 8.

The base bracket 20 arranged on the upper part of the pump portion P is formed in a substantially disk shape. The base bracket 20 has a role of a partition wall that separates the pump portion P and the motor portion M. A bearing portion 34 that rotatably supports the lower end of the rotating shaft 9 is formed at substantially the center of the base bracket 20 in the radial direction.

The bearing portion 34 may be any bearing as long as it can radially support the rotating shaft 9, and various radial sliding bearings can be preferably adopted. In particular, it is preferable to have a material or structure capable of obtaining a lubricating effect by allowing fuel to permeate into the bearing gap. Further, the bearing portion 34 may be fixed to a bearing which is a separate member, or may be formed on the base bracket 20 itself.

A pump casing groove 35 is formed on the lower surface of the base bracket 20 near the outer periphery. The pump casing groove 35 has a substantially arc shape in the radial cross section of the base bracket 20, and is formed so as to draw a C shape in an axial plan view along the outer peripheral portion of the impeller 100 described later. By forming the pump casing groove 35 in a C shape, the pump casing groove 35 has a shape having a start end portion and an end portion (both not shown) in an axial plan view.

Further, the base bracket 20 is formed with a fuel guide hole (not shown) that communicates with the pump casing groove 35 and penetrates the base bracket 20 in the thickness direction at a position corresponding to the end portion of the pump casing groove 35. ing. Therefore, the fuel guide hole is opened inside the motor portion M on the upper surface of the base bracket 20.

The impeller 100 is formed in a substantially disk shape. A shaft hole 39 for connecting the rotating shaft 9 and the impeller 100 so as not to rotate relative to each other is formed at the center of the impeller 100 in the radial direction. The lower end of the rotating shaft 9 penetrates the impeller 100 and projects toward the inlet cover 38.
A large number of blades 40 having an appropriate blade shape arranged at predetermined intervals in the circumferential direction are provided on the outer peripheral portion of the impeller 100. The radial length of the blade 40 is appropriately set according to the width of the radial cross section of the pump casing groove 35.

On the upper surface of the inlet cover 38, a pump casing groove 41, which is a C-shaped groove substantially similar to the pump casing groove 35, is formed from a casing groove start end (not shown) to a casing groove end (not shown). .. The pump casing groove 41 is formed at a position where it vertically overlaps with the pump casing groove 35 of the base bracket 20.

Further, a thrust bearing 42 for rotatably supporting the rotating shaft 9 in the thrust direction is provided at substantially the center of the inlet cover 38 in the radial direction. The thrust bearing 42 may have any material and shape as long as it has an appropriate sliding performance when immersed in fuel. Further, the inlet cover 38 is formed with a suction port (not shown) that penetrates in the axial direction at a position that overlaps with the start end portion (not shown) of the pump casing groove 35 formed in the base bracket 20 in the axial direction. ..
In addition to this, the inlet cover 38 is formed through a degassing hole (not shown) for discharging the vapor generated in the fuel pump 3.

The holder portion 191 including the fuel pump 3 has a flange unit 4 and an upper cup 5. The flange unit 4 is attached to the upper end of the fuel pump 3 and is attached to the fuel tank 2. Further, the upper cup 5 is formed so as to cover the outer peripheral surface of the fuel pump 3.
The flange unit 4 has a resin-made substantially disk-shaped unit body 44. The unit main body 44 is inserted from the outside (upper side) into the opening 2b formed in the upper wall 2a of the fuel tank 2 and attached to the upper wall 2a. A recess 45 is formed in most of the center on the inner surface side of the unit main body 44, and the unit main body 44 is in a state of being composed of a peripheral wall 44a and an end portion (bottom wall) 44b.

A mounting wall 49 having a substantially annular shape in an axial plan view is erected near the outer periphery of the recess 45. The tip surface 49a of the mounting wall 49 serves as a contact surface for the upper cup 5.
Further, in the recess 45, a check valve fitting portion 230 is provided so as to project at a position corresponding to the check valve housing portion 31 of the outlet cover 8. The check valve fitting portion 230 is formed with a stepped recess 230a so as to correspond to the outer shape of the check valve housing portion 31. When the check valve accommodating portion 31 is fitted into the stepped recess 230a, the O-ring 231 is mounted on the stepped surface 31a formed on the outer peripheral surface of the check valve accommodating portion 31, so that the O-ring 231 is mounted on the mating surface of both 230a and 31. It is possible to prevent fuel leakage.

The peripheral wall 44a of the unit main body 44 is provided with a flange portion 47 formed at substantially the center in the axial direction so as to correspond to the opening 2b of the fuel tank 2. The flange portion 47 closes the opening 2b of the fuel tank 2. Two mounting stays 50, which are arranged so as to face each other in the radial direction, are projected from the flange portion 47.

The mounting stay 50 is formed with a recess 48 at the tip through which bolts, screws, and the like can be inserted in the axial direction. A bolt, a screw, or the like is inserted into the recess 48, and the flange unit 4 is fixed to the fuel tank 2 by using a female screw portion, a screw hole, or the like provided on the upper wall 2a of the fuel tank 2. That is, the flange unit 4 is in a state where the upper side of the mounting stay 50 is exposed to the outside of the fuel tank 2.

A fuel take-out pipe 57 is provided above the unit main body 44. The fuel take-out pipe 57 is for pumping the fuel pumped from the fuel pump 3 to the internal combustion engine, and the tip thereof is connected to an internal combustion engine (not shown). An intermediate flow path portion 232 is provided between the fuel take-out pipe 57 and the end portion 44b of the unit main body 44 so as to straddle both 57 and 44. Inside the intermediate flow path portion 232, an intermediate fuel flow path 232a for communicating the fuel flow path 43 in the fuel take-out pipe 57 and the stepped recess 230a of the check valve fitting portion 230 is formed. As a result, the fuel discharged to the outside of the fuel pump 3 (outlet cover 8) through the check valve 32 can be sent out to the fuel flow path 43 of the fuel take-out pipe 57.

The end portion 44b of the unit main body 44 is provided so that the connector 58 faces substantially the horizontal direction on the outer side in the radial direction from the pressure regulator 37. The connector 58 is for supplying electric power of an external power source (not shown) to the fuel supply device 1. A receiving portion 60 is formed in the connector 58 toward the outside. A cable extending from an external power supply (not shown) can be fitted into the receiving portion 60. The connector terminal 59 contained in the connector 58 is formed in a substantially L-shaped cross section. One end of the connector terminal 59 protrudes into the receiving portion 60 of the connector 58, and the other end protrudes into the recess 45 of the unit main body 44.

Here, the other end of the connector terminal 59 and the male terminal 30 provided on the outlet cover 8 of the fuel pump 3 are connected to each other via a lead wire 36. The external power supply and the connector terminal 59 are electrically connected. Further, the connector terminal 59 and the brush (not shown) are electrically connected to the segment 16 via the lead wire 36. Therefore, electric power from an external power source can be supplied to the winding 15 connected to the segment 16. The lead wire 36 is provided with a female terminal (not shown) that can be inserted into and removed from the male terminal 30 at the terminal portion on the male terminal 30 side. On the other hand, a terminal 102 that can be inserted into and removed from the connector terminal 59 is attached to the terminal portion of the lead wire 36 on the connector terminal 59 side.

The upper cup 5 that covers the outer peripheral surface of the fuel pump 3 has a cup body 195 formed in a tubular shape by a resin or the like. The upper cup 5 is formed so that the fuel pump 3 can be inserted from the opening side formed at the lower end of the cup body 195.
The peripheral wall 95b of the cup body 195 extends from the flange unit 4 to substantially the center of the fuel pump 3 in the axial direction. The inner diameter of the peripheral wall 95b is set so as to substantially match the outer diameter of the motor housing 6 of the fuel pump 3 and to a size in which the fuel pump 3 can be inserted. Therefore, almost no gap is formed between the peripheral wall 95b of the cup body 195 and the motor housing 6.

A diameter-expanded portion 101 whose diameter is increased by a step is formed on most of the peripheral wall 95b on the flange unit 4 side. Then, the upper end of the enlarged diameter portion 101 is fixed by welding or the like in a state where it is in contact with the mounting wall 49 of the flange unit 4, and the flange unit 4 and the upper cup 5 are integrated. That is, the diameter of the mounting wall 49 of the flange unit 4 is set to substantially match the diameter of the upper cup 5. Further, a gap is formed between the enlarged diameter portion 101 and the motor housing 6. The inner diameter of the enlarged diameter portion 101 is set so that the size of the gap S between this and the motor housing 6 is large enough to allow the lead wire 36 to pass through.

Further, the peripheral wall 95b of the cup body 195 is provided with a gauge mounting plate 185 extending downward in the axial direction from the peripheral edge of the opening. A sender gauge 193 is attached to the gauge mounting plate 185. The sender gauge 193 is a liquid level gauge that detects the remaining amount of fuel in the fuel tank 2, that is, the liquid level position. The sender gauge 193 is provided at the tip of the gauge body 197 which is attached to the gauge mounting plate 185 and formed in a box shape, the swing arm 198 which is rotatably provided with respect to the gauge body 197, and the swing arm 198. It is equipped with a float 199 that can float on the liquid surface.

A detection board is fixed to the swing arm 198, and a contact point in contact with the detection board is fixed to the gauge body 197. Therefore, when the float 199 moves according to the liquid level, the swing arm 198 that supports the float 199 rotates about the gauge body 197. Since the detection substrate rotates with the rotation of the swing arm 198, the contact points in contact with the detection substrate are switched, and the position of the liquid level can be detected.
Further, since the length of the swing arm 198 is set to a length that allows the float 199 to move according to the position of the liquid level, the remaining fuel remains even when the remaining amount of fuel is low. The amount can be detected accurately.

Further, on the peripheral wall 95b of the cup body 195, three locking pieces 46 extending downward in the axial direction from the peripheral edge of the opening are formed at three points at equal intervals in the circumferential direction.
The locking piece 46 is formed so as to be elastically deformable in a direction in which the tip thereof expands in diameter toward the outside in the radial direction. The locking piece 46 supports the fuel pump 3 by snap-fitting to the filter unit 192. Therefore, the fuel pump 3 is supported by the filter unit 192 without the fuel supply device 1 expanding in the radial direction.
The locking piece 46 extends slightly below the pump portion P of the fuel pump 3. A locking hole 62 is formed in the locking piece 46 at a position corresponding to a support plate 182 described later in the filter unit 192.

A filter unit 192 is provided below the pump portion P on the suction side of the fuel pump 3. The filter unit 192 is provided on the lower surface of the pump portion P, has a support plate 182 that is snap-fitted to the locking piece 46 of the upper cup 5, and a suction filter 51 that filters the fuel in the fuel tank 2 and guides it to the pump portion P. And a suction port 53 provided between the support plate 182 and the suction filter 51.

The support plate 182 is formed in a substantially disk shape. On the outer peripheral surface 182a of the support plate 182, three locking convex portions 180 that can be locked with the locking hole 62 are formed at a portion corresponding to the locking hole 62 of the locking piece 46. As a result, the support plate 182 is positioned in the axial direction Z and the circumferential direction θ. Further, the upper end surface of the support plate 182 is formed so as to support the fuel pump 3. Therefore, the fuel pump 3 is in a state of being supported by the holder portion 191 via the support plate 182 of the filter unit 192.

The suction filter 51 is composed of a filter medium 51a and a welded portion 51b formed by welding the outer peripheral edge of the filter medium 51a. The filter medium 51a is, for example, a bent mesh nylon cloth, and is formed in a bag shape.
On the other hand, the welded portion 51b is formed by welding the outer peripheral edge of the bag-shaped filter medium 51a, for example, and prevents the bag-shaped filter medium 51a from opening. The suction port 53 is formed in a substantially cylindrical shape. Both ends of the suction port 53 communicate with the support plate 182 and the suction filter 51, respectively. The support plate 182, the suction filter 51, and the suction port 53 are integrated by welding. Therefore, the number of parts can be reduced and the assembling property can be improved.

Here, on the base end side of the fuel take-out pipe 57 provided in the unit main body 44, a pressure regulator storage recess 54 for communicating the fuel flow path 43 and the recess 45 of the unit main body 44 is along the axial direction. It is formed. The pressure regulator 37 is housed in the pressure regulator storage recess 54. The pressure regulator 37 returns the fuel in the fuel flow path 43 to the fuel tank 2 when excess pressure is applied in the fuel flow path 43 of the fuel take-out pipe 57, and keeps the fuel pressure constant at all times. be.

The pressure regulator 37 is housed in a bottomed tubular pressure regulator support portion 52 formed so as to surround the pressure regulator 37, and is inserted into the pressure regulator storage recess 54 from the recess 45 side in this state. An O-ring 234 is interposed between the pressure regulator storage recess 54 and the pressure regulator 37.
The lower portion of the pressure regulator support portion 52 is in a state of protruding toward the recess 45 side of the unit main body 44. A through hole 233 is formed in the lower surface 52a of the pressure regulator support portion 52, from which fuel is discharged when excess pressure is applied.

(Pressure regulator)
FIG. 3 is a perspective view of the pressure regulator 37.
As shown in FIG. 3, the pressure regulator 37 includes a case 61 and a pressure regulator main body 63 (pressure control device main body). The pressure regulator main body 63 is provided in the case 61.

The case 61 includes a case main body 65, a case upper portion 67 (case one side portion), and a case lower portion 69 (case other side portion). The case body 65, the case upper portion 67, and the case lower portion 69 are integrally molded with resin. A low swelling resin is used as the resin. Examples of the low swelling resin include PPS resin (polyphenylene sulfide resin).

The case body 65 is formed in a cylindrical shape. The upper end of the outer peripheral surface 83 of the case body 65 is formed so as to extend downward from the upper end toward the outer peripheral side of the case 61. The case upper side portion 67 is connected to the upper side of the case main body 65 with a gap S1. The outer diameter of the case upper portion 67 is set to be larger than that of the case main body 65. The case upper portion 67 includes a first upper portion 71, a second upper portion 73, a third upper portion 75, and a plurality of leg portions 77.

The first upper portion 71 is formed in an annular shape. The first upper portion 71 is arranged on the upper side of the case main body 65 with a gap S1. The outer diameter of the first upper portion 71 is the maximum outer diameter of the case upper portion 67. The second upper portion 73 is formed in a cylindrical shape. The second upper portion 73 is coupled to the upper side of the first upper portion 71. The outer diameter of the second upper portion 73 is set to be smaller than that of the first upper portion 71. The third upper portion 75 is formed in a cylindrical shape. The third upper portion 75 is coupled to the upper side of the second upper portion 73. The outer diameter of the third upper portion 75 is set to be smaller than that of the second upper portion 73. The above-mentioned O-ring 234 is fitted on the outer peripheral side of the lower portion of the third upper portion 75.

The plurality of leg portions 77 are provided at equal intervals in the circumferential direction θ of the lower surface of the first upper portion 71. The upper end of each leg portion 77 is connected to the lower surface of the first upper portion 71. Each leg portion 77 is formed so as to extend downward from the lower surface of the first upper portion 71. Each leg 77 is connected to the outer peripheral surface 83 of the case body 65 on the inner side surface 81. The lower end 85 of each leg 77 and the lower end 87 of the case body 65 are set at the same height position. The outer surface 89A of each leg portion 77 is set to be flush with the outer peripheral surface 89 of the first upper portion 75.

The lower portion 69 of the case is formed in a cylindrical shape. The lower case portion 69 is coupled to the lower side of the case body 65. The lower side portion 69 of the case has the same outer diameter as the case main body 65. As a result, the outer diameter of the lower case portion 69 is set to be smaller than that of the case upper portion 67. As a result, a space portion S3 is formed between the outer peripheral surface 83 of the case main body 65 and the case lower portion 69 and the outer peripheral surface 89 of the first upper portion 71 of the case upper portion 67.

FIG. 4 is a cross-sectional view of the pressure regulator 37 along the axial direction Z.
As shown in FIG. 4, the pressure regulator 37 is in contact with the first upper portion 71 and the outer surfaces 89A of the plurality of leg portions 77 in a state of being inserted into the fuel flow path 43. A gangway 91 is provided inside the case 61. The gangway 91 is provided so as to penetrate the inside of the case 61 from the upper end to the lower end along the axial direction Z. A closed portion 93 is provided at an intermediate portion of the gangway 91 in the axial direction Z. The blocked portion 93 is a portion that is closed by a valve 107, which will be described later.

As a result, the through-passage 91 is composed of the through-passage 91 of the case upper portion 67, the closed portion 93, the through-passage 91 of the case main body 65, and the through-passage 91 of the case lower portion 69. A locking portion 133 is provided in the circumferential direction θ of the lower portion of the inner peripheral surface 131 of the through-passage 91 of the case upper portion 67. The locking portion 133 is formed in an annular shape. A through hole 135 is provided through the central portion of the locking portion 133. A pressing protrusion 137 is formed in the circumferential direction θ of the lower surface of the locking portion 133. The pressing protrusion 137 is formed in an annular shape. The pressing protrusion 137 is formed so as to project downward from the lower surface of the locking portion 133. The height (length in the axial direction Z) from the lower surface of the pressing protrusion 137 is, for example, 0.5 mm.

One end of a plurality of radial flow paths 95 is connected to the closed portion 93. Each radial flow path 95 is provided inside the case 61 along the radial direction R. The other end of each radial flow path 95 is open to the outer peripheral side of the case 61. The radial flow path 95 is a flow path for flowing fuel from the gangway 91 along the radial direction R to the outer peripheral side of the case 61.

One end of the axial flow path 97 is connected to the other end side of each radial flow path 95. The axial flow path 97 is provided inside the case 61 along the axial direction Z. The other end of the axial flow path 97 is open to the lower end side of the case 61. The axial flow path 97 is a flow path for flowing fuel from the other end side of the radial flow path 95 to the lower end side of the case 61 along the axial direction Z.

The closed portion 93 of the gangway 91 is formed by a gap S1 between the case main body 65 and the case upper portion 67. Each radial flow path 95 is composed of a gap S1 and an inner peripheral surface 171 of the fuel flow path 43. The axial flow path 97 is composed of a space portion S3 on the outer peripheral side of the case main body 65 and the case lower portion 69, and an inner peripheral surface 171 of the fuel flow path 43.

The inner peripheral side surface 83A on one end side of the axial flow path 97 is the upper end portion of the outer peripheral surface 83 of the case body 65. The upper end portion of the outer peripheral surface 83 is formed so as to extend downward from the upper end toward the outer peripheral side of the case 61 as described above. Therefore, the inner peripheral side surface 83A on one end side of the axial flow path 97 is formed so as to extend inward in the radial direction R.

The pressure regulator main body 63 closes the closed portion 93 and one end of the plurality of radial flow paths 95. As a result, fuel passing through the second fuel supply path 47 flows in and is stored in the through-passage 91 of the case upper portion 67 formed above the blocked portion 93. The pressure regulator main body 63 is arranged below the closed portion 93 of the gangway 91. The pressure regulator main body 63 opens one end of the blocked portion 93 and the plurality of radial flow paths 95 when the pressure of the fuel stored in the through-passage 91 of the case upper portion 67 exceeds a predetermined pressure. The pressure regulator main body 63 closes one end of the closed portion 93 and the plurality of radial flow paths 95 when the fuel pressure becomes equal to or lower than a predetermined pressure. The specific configuration of the pressure regulator main body 63 will be described below.

The pressure regulator main body 63 includes a valve unit 103 and a drive unit 105. The valve unit 103 includes a valve 107 and a pressed portion 109. The valve 107 is made of rubber. The valve 107 closes one end of the closed portion 93 and the plurality of radial flow paths 95. The valve 107 is arranged so as to be movable in the axial direction Z on the lower side from the closed portion 93. The valve 107 includes a base 111, a protrusion 113, and a press-fitting portion 115.

The base 111 is formed in the shape of a circular plate. The base portion 111 closes the through hole 135 of the locking portion 133 in the through passage 91 of the case upper portion 67. The outer peripheral side of the upper surface 117 of the base portion 111 is pressed by the pressing projection 137 of the locking portion 133 and locked to the locking portion 133. The pressing protrusion 137 bites the outer peripheral side of the upper surface 117 by, for example, 0.1 mm and presses it. The protrusion 113 is provided at the center of the upper surface 117 of the base 111. The protrusion 113 is arranged in the through hole 135 of the locking portion 133. The press-fitting portion 115 is provided at the central portion of the lower surface 119 of the base portion 111. The press-fitting portion 115 is formed so that the cross-sectional shape along the axial direction Z is convex.

FIG. 5 is a bottom view of the valve 107.
As shown in FIG. 5, the above-mentioned press-fitting portion 115 is provided in the central portion of the lower surface 119 (bottom surface) of the base portion 111. The press-fitting portion 115 is formed in an annular shape. The press-fitting portion 115 includes a plurality of first press-fitting portions 121 and a plurality of second press-fitting portions 123. The plurality of first press-fitting portions 121 and the plurality of second press-fitting portions 123 are alternately provided in the circumferential direction θ of the lower surface 119. Three of the plurality of first press-fitting portions 121 and the plurality of second press-fitting portions 123 are arranged at equal intervals in the circumferential direction θ of the lower surface 119. Each of the plurality of first press-fitting portions 121 is formed in an arc shape in a plan view. Each of the plurality of second press-fitting portions 123 is formed in a V shape recessed toward the center in a plan view. The plurality of first press-fitting portions 121 and the plurality of second press-fitting portions 123 are formed by being connected in an annular shape in the circumferential direction θ. As a result, the shape of the press-fitting portion 115 in a plan view is a three-pronged shape.

As shown in FIG. 4, the pressed portion 109 is provided on the lower side of the valve 107. The pressed portion 109 is made of resin. A low swelling resin is used as the resin. Examples of the low swelling resin include PPS resin (polyphenylene sulfide resin). The pressed portion 109, together with the valve 107, closes one end of the closed portion 93 and the plurality of radial flow paths 95. The pressed portion 109 is arranged so as to be movable in the axial direction Z on the lower side from the closed portion 93. The pressed portion 109 includes a base portion 125, a first support portion 127, and a second support portion 129.

The base 125 is formed in a substantially circular plate shape. A press-fitting portion 143 is provided at the center of the upper surface 141 of the base portion 125. The press-fitting portion 115 of the valve 107 is press-fitted and fitted into the press-fitting portion 143. The press-fitted portion 143 is formed so that the cross-sectional shape along the axial direction Z is concave. The press-fitted portion 143 is formed to have the same shape as the press-fitted portion 115 in a plan view (see FIG. 5). The inner diameter of the press-fitted portion 143 is set to be substantially the same as the outer diameter of the press-fitted portion 115. The first support portion 127 is coupled to the central portion of the lower surface 145 of the base portion 125. The first support portion 127 is formed in a substantially columnar shape. The second support portion 129 is coupled to the lower side of the first support portion 127. The second support portion 129 is formed in the shape of a round bar extending along the axial direction Z.

FIG. 6 is a perspective view of the pressed portion 109 as viewed from below.
As shown in FIG. 6, a plurality of slits 149 are provided on the outer peripheral surface 147 of the base 125. The plurality of slits 149 are formed along the axial direction Z of the outer peripheral surface 147. FIG. 7 is a bottom view of the pressed portion 109. As shown in FIG. 7, the plurality of slits 149 are arranged at equal intervals in the circumferential direction θ of the outer peripheral surface 147 of the base portion 125.

As shown in FIG. 4, the drive unit 105 includes a coil spring 173 and a retainer 175.

The coil spring 173 is extrapolated and supported by the pressed portion 109 from below the pressed portion 109. Specifically, the coil spring 173 is extrapolated from the lower side of the second support portion 129 to the second support portion 129 and the first support portion 127, and is abutted against the lower surface 145 of the base portion 125 to be supported by the pressed portion 109. Has been done.

The retainer 175 is press-fitted into the through-passage 91 of the lower portion 69 of the case from below. The retainer 175 is formed in a cylindrical shape with an open upper surface. The retainer 175 closes the opening on the lower side of the gangway 91. A pressing portion 177 is provided inside the retainer 175. The pressing portion 177 is formed so that the cross-sectional shape along the axial direction Z is U-shaped. The pressing portion 177 presses the coil spring 173 upward. As a result, the coil spring 173 is contracted and has a predetermined urging force (predetermined pressure). The coil spring 173 presses the base 125 of the pressed portion 109 with a predetermined urging force, thereby urging the valve 107 upward. As a result, the valve 107 is locked in a state of being pressed by the pressing protrusion 137 of the locking portion 133.

The fuel stored in the gangway 91 of the upper portion 67 of the case presses the valve 107 downward (in a direction that opposes a predetermined urging force of the coil spring 173). When the pressure of the fuel, that is, the pressing force of the fuel pressing the valve 107 downward exceeds the predetermined urging force of the coil spring 173, the drive unit 105 moves the valve unit 103 downward to be blocked. It is configured to open one end of the portion 93 and the plurality of radial flow paths 95. When the fuel pressure becomes equal to or lower than the predetermined urging force, the drive unit 105 moves the valve unit 103 upward by the urging force of the coil spring 173, and the valve 107 is locked to the locking portion 133. It is configured to close one end of the closed portion 93 and the plurality of radial flow paths 95.

In the fuel supply device 1 configured as described above, a method of supplying fuel to the internal combustion engine will be described.
When the motor unit M of the fuel pump 3 is driven, the rotating shaft 9 rotates, and the impeller 100 connected to the rotating shaft 9 so as not to rotate relative to the rotating shaft 9 rotates. When the impeller 100 rotates, the fuel in the fuel tank 2 is sucked from the suction port 53 in a state of being filtered through the suction filter 51.
Since the suction port 53 is connected to a suction port (not shown) formed on the inlet cover 38, the pump unit P sucks fuel from the suction port (not shown), and the blades 40 inside the pump casing grooves 35 and 41. While boosting the fuel pressure, the fuel is discharged into the motor unit M through a fuel guide hole (not shown).

The fuel discharged into the motor unit M flows between the adjacent permanent magnets 19 and 19 and between the permanent magnet 19 and the armature 7 to the discharge port 33. Then, the fuel is conveyed to the fuel flow path 43 of the fuel take-out pipe 57 through the discharge port 33 and the check valve 32. Here, when the fuel pressure of the fuel flow path 43 is higher than a predetermined value, the fuel is discharged from the inner surface side of the flange unit 4 via the pressure regulator 37 and returned to the fuel tank 2 through the upper cup 5. .. On the other hand, when the fuel pressure of the fuel flow path 43 is within a predetermined range, the fuel is conveyed to an internal combustion engine (not shown) through the fuel take-out pipe 57.

Next, the method of controlling the fuel pressure by the pressure regulator 37 will be described in more detail.
A part of the fuel passing through the fuel flow path 43 flows into the through-passage 91 of the upper side portion 67 of the case and is stored. As the pressure of the fuel passing through the fuel flow path 43 increases, the pressure of the fuel stored in the through-passage 91 of the upper portion 67 of the case also increases.

When the pressure of the fuel stored in the through-passage 91 of the case upper portion 67 exceeds the predetermined urging force of the coil spring 173, the pressure regulator main body 63 sets the valve unit 103 as shown in FIGS. 4 to 8. It is moved downward to open one end of the closed portion 93 and the plurality of radial flow paths 95. As a result, the fuel G flows out from the gangway 91 into each radial flow path 95, flows to the outer peripheral side of the case 61, and flows into the axial flow path 97. The fuel that has flowed into the axial flow path 97 flows to the lower end side of the case 61 and is discharged to the outside of the case 61.

The fuel G discharged to the outside of the case 61 is discharged from the inner surface side of the flange unit 4 and returned to the fuel tank 2 through the upper cup 5. As a result, the pressure of the fuel stored in the gangway 91 of the upper portion 67 of the case is reduced. As a result, the pressure of the fuel pumped from the fuel supply device 1 to the internal combustion engine also decreases. The pressure regulator main body 63 moves the valve unit 103 upward by the urging force of the coil spring 173 when the pressure of the fuel stored in the through-passage 91 of the case upper portion 67 becomes equal to or less than a predetermined urging force. Close one end of the closed portion 93 and the plurality of radial flow paths 95.

Next, the operation and effect of the pressure regulator 37 of the present embodiment will be described.

(1) The pressure regulator 37 of the present embodiment includes a case 61 and a gangway 91 provided so as to penetrate the inside of the case 61 along the axial direction Z. The pressure regulator 37 of the present embodiment includes a valve 107 that rotatably closes the closed portion 93 set in the gangway 91, and a pressed portion 109 provided under the valve 107. .. The pressure regulator 37 of the present embodiment includes a drive unit 105 arranged in the gangway 91 in a state where the pressed portion 109 is pressed by a predetermined urging force (predetermined pressure) from the lower side of the pressed portion 109. When the pressure of the fuel G stored above the blocked portion 93 of the gangway 91 exceeds a predetermined urging force, the drive unit 105 moves the pressed portion 109 and the valve 107 downward to be blocked. Part 93 opens. A plurality of first press-fitting portions 121 and a plurality of second press-fitting portions 123 are alternately provided on the lower surface 119 of the valve 107 in the circumferential direction θ. The upper surface 141 of the pressed portion 109 is provided with a press-fit portion 143 in which a plurality of first press-fit portions 121 and a plurality of second press-fit portions 123 are press-fitted. The plurality of second press-fitting portions 123 are press-fitted more loosely with respect to the press-fitting portion 143 than the plurality of first press-fitting portions 121.

In the pressure regulator 37 of the present embodiment, since the valve 107 and the pressed portion 109 are fitted by press fitting, a sufficient assembling force between the valve 107 and the pressed portion 109 is secured. Therefore, no adhesive is required for assembling the valve 107 and the pressed portion 109, so that the work of applying the adhesive is not required. Therefore, in the manufacture of the pressure regulator 37, it is possible to shorten the time required for assembling the valve 107 and the pressed portion 109. Therefore, the pressure regulator 37 of the present embodiment can improve the manufacturing efficiency.

In the pressure regulator 37 of the present embodiment, since the second press-fitting portion 123 is press-fitted more loosely to the press-fitting portion 143 than the first press-fitting portion 121, when the valve 107 swells, the swelling portion is transferred to the second press-fitting portion 123. It becomes possible to allow between the press-fitted portion 143 and the press-fitted portion 143. Therefore, even if the valve 107 swells, it is suppressed that the shape of the entire valve 107 becomes large, so that the gangway 91 is prevented from becoming more occluded than usual. As a result, even if the pressure of the fuel G exceeds a predetermined urging force, the valve 107 moves sufficiently downward, so that it is suppressed that the fuel G stored in the gangway 91 takes a long time to flow out, and the fuel G of the fuel G. It is suppressed that it takes time to reduce the pressure. Therefore, the pressure regulator 37 of the present embodiment can suppress a decrease in the pressure control function of the fuel G even if the valve 107 swells.

Further, since the pressed portion 109 has a lower swelling property than the valve 107, the pressed portion 109 does not swell even if the valve 107 swells, and only the swelled portion of the valve 107 is referred to as the second press-fitting portion 123. It becomes possible to surely allow the valve with the press-fitted portion 143. Therefore, even if the valve 107 swells, it is further suppressed that the shape of the entire valve 107 becomes large, and the obstruction of the gangway 91 becomes higher than usual. Therefore, the pressure regulator 37 of the present embodiment can suppress a decrease in the pressure control function of the fuel G even if the valve 107 swells.

(2) In the pressure regulator 37 of the present embodiment, at least three of the plurality of first press-fitting portions 121 and the plurality of second press-fitting portions 123 are arranged at equal intervals in the circumferential direction θ. As a result, when the valve 107 swells, the swelling portion can be allowed between the second press-fitted portion 123 and the press-fitted portion 143 over the entire circumference of the valve 107. Therefore, even if the valve 107 swells, it is further suppressed that the shape of the entire valve 107 becomes large. As a result, even if the pressure of the fuel G exceeds the imposition force, the valve 107 moves more sufficiently to the lower side, so that it is further suppressed that the fuel G stored in the gangway 91 takes a long time to flow out, and the fuel G is further suppressed. It is further suppressed that it takes time to reduce the pressure of the fuel. Therefore, the pressure regulator 37 of the present embodiment can further suppress a decrease in the pressure control function of the fuel G even if the valve 107 swells.

Further, since the plurality of first press-fitting portions 121 and the plurality of second press-fitting portions 123 are arranged at equal intervals in the circumferential direction θ, the valve 107 is covered with the valve 107 when the pressed portion 109 is fitted. Since the force applied from the pressing portion 109 is dispersed, the pressed portion 109 is stably fitted to the valve 107, so that it is possible to suppress the influence on the pressure control function. Further, the plurality of first press-fitting portions 121 and the plurality of second press-fitting portions 123 are provided in the central portion of the lower surface 119 of the valve 107, and the press-fitting portion 143 is located in the central portion of the upper surface 141 of the pressed portion 109. It is provided. Therefore, the axis of the valve 107 and the pressed portion 109 can be easily aligned.

(3) In the pressure regulator 37 of the present embodiment, the plurality of first press-fitting portions 121 and the plurality of second press-fitting portions 123 are formed so that the cross-sectional shape along the axial direction Z is convex. The press-fitted portion 143 is formed so that the cross-sectional shape along the axial direction Z is concave. As a result, the valve 107 and the pressed portion 109 can be assembled in a shape that is easy to manufacture, so that the cost required for assembly can be suppressed. Therefore, the pressure regulator 37 of the present embodiment can suppress the manufacturing cost.

(4) In the pressure regulator 37 of the present embodiment, the plurality of first press-fitting portions 121 and the plurality of second press-fitting portions 123 are formed by being annularly connected in the circumferential direction θ. As a result, the plurality of first press-fitting portions 121 and the plurality of second press-fitting portions 123 can be easily press-fitted into the press-fitting portion 143 because the press-fitting positions can be easily adjusted with respect to the press-fitting portion 143. It becomes possible to match. Therefore, in the manufacture of the pressure regulator 37, the time required for assembling the valve 107 and the pressed portion 109 can be further shortened. Therefore, the pressure regulator 37 of the present embodiment can further improve the manufacturing efficiency.

(5) In the pressure regulator 37 of the present embodiment, the case 61 has a lower swelling property than the valve 107. The inner peripheral surface 131 above the closed portion 93 of the gangway 91 is provided with a locking portion 133 that presses and locks the upper surface 117 of the valve 107 over the entire circumference. As a result, even if the valve 107 swells, the locking portion 133 does not swell, so that the pressing state of the locking portion 133 against the valve 107 is maintained. Therefore, the pressure regulator 37 of the present embodiment can prevent a decrease in the blockage of the gangway 91 even if the valve 107 swells.

(6) In the pressure regulator 37 of the present embodiment, a protrusion 113 is provided on the upper surface 117 of the valve 107. As a result, when the pressure of the fuel G is controlled, the fuel G stored in the gangway 91, as shown in FIG. 8, hits the protrusion 113 when flowing out of the gangway 91 and flows to the outer peripheral side of the valve 107. Therefore, the pressure regulator 37 of the present embodiment can efficiently flow out the fuel G to the outer peripheral side of the valve 107 and efficiently reduce the pressure of the fuel G as compared with the case where the protrusion 113 is not provided. Therefore, the pressure regulator 37 of the present embodiment can efficiently control the pressure of the fuel G.

(7) The pressure regulator 37 of the present embodiment includes a case 61 and a gangway 91 provided so as to penetrate the inside of the case 61 along the axial direction Z. The pressure regulator 37 of the present embodiment includes a radial flow path 95 having one end connected to a closed portion 93 set in the gangway 91 and provided inside the case 61 along the radial direction R. The pressure regulator 37 of the present embodiment has one end connected to the other end side of the radial flow path 95 and is provided inside the case 61 along the axial direction Z, and the other end opens to the other end side of the case 61. The axial flow path 97 is provided. The pressure regulator 37 of the present embodiment includes a pressure regulator main body 63 that is arranged below the closed portion 93 of the gangway 91 by closing one end of the closed portion 93 and the radial flow path 95 so as to be openable and closable. .. When the pressure of the fuel G stored above the closed portion 93 of the gangway 91 exceeds a predetermined urging force (predetermined pressure), the pressure regulator main body 63 of the closed portion 93 and the radial flow path 95 Open one end.

As a result, when the pressure of the fuel G stored in the gangway 91 exceeds a predetermined pressure, the fuel G flows in the radial flow path 95 and the axial flow path 97 in this order, and is discharged to the other end side of the case 61. Therefore, the fuel G can flow along the axial direction Z on the outer peripheral side of the gangway 91, so that the fuel G flows between the gangway 91 and the pressure regulator main body 63 along the axial direction Z. It is suppressed. Therefore, the shaking of the pressure regulator main body 63 is suppressed, and the pressure regulator main body 63 is suppressed from hitting the case 61 (case main body 65). Therefore, the pressure regulator 37 of the present embodiment can suppress the generation of abnormal noise when the pressure of the fuel G is controlled. In the pressure regulator 37 of the present embodiment, the outflow direction of the fuel G stored in the gangway 91 is one direction of the radial direction R, so that the fuel G can be stably discharged. The pressure of G can be reduced without wobbling.

(8) In the pressure regulator 37 of the present embodiment, the case 61 has a case body 65 and a case upper portion 67 formed with a gap S1 on the upper side of the case body 65 and having an outer diameter larger than that of the case body 65. Be prepared. The gap S1 constitutes a closed portion 93 of the gangway 91 and a radial flow path 95. The space portion S3 formed between the outer peripheral surface 83 of the case main body 65 and the outer peripheral surface 89 of the case upper portion 67 constitutes an axial flow path 97. As a result, the radial flow path 95 and the axial flow path 97 can be formed without significantly processing the case 61. Therefore, the pressure regulator 37 of the present embodiment can suppress the generation of abnormal noise when the pressure of the fuel G is controlled while suppressing the manufacturing cost of the case 61.

(9) In the pressure regulator 37 of the present embodiment, the case lower portion 69 is formed on the lower side of the case main body 65 in the case 61. The outer diameter of the lower case portion 69 is set to be smaller than that of the case upper portion 67. This makes it possible to suppress sink marks when the case 61 is integrally molded. Therefore, the pressure regulator 37 of the present embodiment can suppress molding defects of the case 61.

(10) In the pressure regulator 37 of the present embodiment, the inner peripheral side surface 83A on one end side of the axial flow path 97 is formed so as to extend inward in the radial direction R. As a result, the fuel G that has flowed into the radial flow path 95 can easily flow into the axial flow path 97. Therefore, the fuel G is further suppressed from flowing along the axial direction Z between the gangway 91 and the pressure regulator main body 63. Therefore, the shaking of the pressure regulator main body 63 is further suppressed, and the pressure regulator main body 63 is further suppressed from hitting the case 61. Therefore, the pressure regulator 37 of the present embodiment can further suppress the generation of abnormal noise when the pressure of the fuel G is controlled.

(11) In the pressure regulator 37 of the present embodiment, the pressure regulator main body 63 is provided below the valve 107 and the valve 107 that block one end of the closed portion 93 of the gangway 91 and the radial flow path 95. It is provided with a pressed portion 109. Further, the pressure regulator main body 63 includes a drive unit 105 arranged in the gangway 91 in a state where the pressed portion 109 is pressed by a predetermined urging force from the lower side of the pressed portion 109. When the fuel pressure exceeds a predetermined urging force, the drive unit 105 moves the pressed portion 109 and the valve 107 downward to open one end of the blocked portion 93 and the radial flow path 95. A slit 149 is formed on the outer peripheral surface 147 of the pressed portion 109 along the axial direction Z.

As a result, when the pressure of the fuel G is controlled, even if the fuel G in the gangway 91 hits the outer peripheral surface 147 of the pressed portion 109, the fuel G escapes to the lower side of the pressed portion 109 through the slit 149. Therefore, it is possible to prevent the fuel G from adhering to the outer peripheral surface 147 of the pressed portion 109. As a result, the pressed portion 109 can move smoothly in the axial direction Z, so that the valve 107 can smoothly open one end of the closed portion 93 and the radial flow path 95. Therefore, the pressure regulator 37 can smoothly discharge the fuel G in the gangway 91 to the outside of the case 61 via the radial flow path 95 and the axial flow path 97, and can efficiently reduce the pressure of the fuel G. become. Therefore, the pressure regulator 37 of the present embodiment can efficiently control the pressure of the fuel G.

Further, since the slits 149 are arranged at equal intervals in the circumferential direction θ of the outer peripheral surface 147 of the pressed portion 109, it is possible to secure a constant gap between the pressed portion 109 and the case 61. As a result, the pressed portion 109 can move more smoothly in the axial direction Z. Therefore, the fuel G in the gangway 91 can be discharged to the outside of the case 61 more smoothly, and the pressure of the fuel G can be lowered more efficiently. Therefore, the pressure regulator 37 of the present embodiment can more efficiently control the pressure of the fuel G.

(12) The fuel supply device 1 of the present embodiment is a fuel supply device 1 that pumps fuel G, which is a fluid, to an internal combustion engine, and includes a pressure regulator that controls the pressure of the fuel G that is pressure-fed to the internal combustion engine. Therefore, the pressure regulator 37 of the present embodiment is used as the pressure regulator. As a result, the fuel supply device 1 of the present embodiment can suppress the generation of abnormal noise when the pressure of the fuel G is controlled in the pressure regulator 37.

Further, the fuel supply device 1 of the present embodiment can improve the manufacturing efficiency of the pressure regulator 37 by using the pressure regulator 37 of the present embodiment. Therefore, the fuel supply device 1 of the present embodiment can improve the manufacturing efficiency of the entire fuel supply device 1. Further, the fuel supply device 1 of the present embodiment can suppress a decrease in the pressure control function of the fuel G even if the valve 107 of the pressure regulator 37 swells.

Although the embodiments of the present invention have been described in detail with reference to the drawings, the specific configuration is not limited to this embodiment, and design changes that do not deviate from the gist of the present invention are made in the present invention. included.

In the present embodiment, as shown in FIG. 5, the press-fitting portion 115 of the valve 107 is formed so as to have a three-pronged shape in a plan view, but the shape of the press-fitting portion 115 is not limited to the shape of the present embodiment. For example, a shape such as the press-fitting portion 215 of the valve 207 shown in FIG. 9 may be used. In the present embodiment, the outer diameter of the lower case portion 69 is the same as the outer diameter of the case main body 65, but the outer diameter is not necessarily the same, and the outer diameter of the case lower portion 69 is the outer diameter of the case upper portion 67. It should be smaller than the outer diameter.

In the pressure regulator 37 of the present embodiment, the pressure regulator 37 is used for the bottom-mounted fuel supply device 1 attached to the bottom wall of the fuel tank, but it can also be used for the top-mounted fuel supply device mounted on the top wall of the fuel tank. good. The pressure regulator 37 of the present embodiment is provided by branching from the fuel flow path 43 through which the fuel G discharged from the fuel pump 3 passes, but the present invention is not limited to this, and can be applied to various hydraulic circuits. Further, in the present embodiment, the case where the fluid to be pressure controlled is the fuel of the vehicle has been described, but the present invention is not limited to this, and may be applied to water, air, hydraulic oil of a hydraulic circuit, and the like. can.

1 ... Fuel supply device 37 ... Pressure regulator (pressure control device)
61 ... Case 91 ... Through-passage 93 ... Closed part 105 ... Drive part 107 ... Valve 109 ... Pressed part 113 ... Protrusion 117 ... Upper surface of the valve (one side surface in the axial direction)
119 ... The lower surface of the valve (the other side surface in the axial direction)
121 ... 1st press-fitting portion 123 ... 2nd press-fitting portion 131 ... Inner peripheral surface of the gangway 133 ... Locking portion 141 ... Upper surface of the pressed portion (one side surface in the axial direction)
143 ... Press-fitted portion G ... Fuel Z ... Axial direction θ ... Circumferential direction

Claims (7)

With the case
A gangway that penetrates the inside of the case along the axial direction and
A valve that can open and close the closed part set in the gangway, and
A pressed portion provided on the other side of the valve in the axial direction, and a pressed portion.
The pressed portion is placed in the gangway in a state where the pressed portion is pressed with a predetermined pressure from the other side of the pressed portion in the axial direction, and is stored on one side of the gangway in the axial direction with respect to the blocked portion. A pressure control device including a pressed portion and a driving portion that moves the valve to the other side in the axial direction to open the closed portion when the pressure of the fluid exceeds the predetermined pressure.
On the other side surface of the valve in the axial direction, a plurality of first press-fitting portions and a plurality of second press-fitting portions recessed toward the center in a plan view in the axial direction are alternately provided in the circumferential direction and are annular. It is formed by being connected to
Wherein one side of the axial direction of the pressing portion, the pressure control device, characterized in that the press-fit portion first press-fitting portion of the plurality of that is press-fitted is provided. The pressure control device according to claim 1, wherein at least three of the plurality of first press-fitting portions and the plurality of second press-fitting portions are arranged at equal intervals in the circumferential direction. The plurality of first press-fitting portions and the plurality of second press-fitting portions are formed so that the cross-sectional shape along the axial direction is convex.
The pressure control device according to claim 1 or 2, wherein the press-fitted portion is formed so that the cross-sectional shape along the axial direction is concave. The method according to any one of claims 1 to 3, wherein the plurality of first press-fitting portions and the plurality of second press-fitting portions are formed by being connected in a ring shape in the circumferential direction. Pressure control device. The case has a lower swelling property than the valve and has a lower swelling property.
On the inner peripheral surface on one side of the through-passage in the axial direction from the closed portion, a locking portion that presses and locks the one side surface in the axial direction of the valve over the entire circumference is provided. The pressure control device according to any one of claims 1 to 4, wherein the pressure control device is provided. The pressure control device according to any one of claims 1 to 5, wherein a protrusion is provided on one side surface of the valve in the axial direction. A fuel supply device that pumps fluid fuel to a supply destination.
A pressure control device for controlling the pressure of fuel pumped to the supply destination is provided, and the pressure control device according to any one of claims 1 to 6 is used as the pressure control device. A fuel supply device characterized by being present.

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