JP5530786B2 - Pressure holding valve inspection device and inspection method - Google Patents

Description

  The present invention relates to an inspection device, an inspection method, and a pressing device for inspecting the pressure holding performance of a pressure holding valve provided in a fuel supply system of an internal combustion engine (hereinafter referred to as “engine”).

Conventionally, a fuel supply system for supplying fuel to an engine pressurizes fuel supplied from a fuel tank with a high-pressure pump and stores it in a delivery pipe. The high-pressure fuel stored in the delivery pipe is transferred from the injector to each cylinder of the engine. It is sprayed in.
In the fuel supply system described in Patent Document 1, a pressure holding valve is provided in a fuel passage that connects a pressurizing chamber that pressurizes fuel of a high-pressure pump and a delivery pipe. The pressure holding valve is composed of a relief valve and a constant residual pressure valve provided inside the valve body of the relief valve.
In general, the relief valve is set to open at a fuel pressure higher than the fuel pressure of the delivery pipe during normal operation of the engine and lower than a fuel pressure at which the electromagnetic injector cannot inject fuel. As a result, the fuel pressure of the delivery pipe becomes an abnormally high pressure and the injector is prevented from being unable to inject fuel.
The constant residual pressure valve is set so as to hold the fuel pressure in the delivery pipe at a predetermined pressure. This predetermined pressure is a pressure at which the vapor generated in the delivery pipe becomes less than the allowable value due to the increase in the fuel pressure in the delivery pipe accompanying the temperature increase in the engine room after the engine is stopped, and the fuel leakage from the injector is less than the allowable value. is there.

In the manufacturing process, the above-described constant residual pressure valve is formed by forming a valve seat on which the valve body of the constant residual pressure valve is seated in an inner passage formed inside the valve body of the relief valve, and then pressing the valve seat to improve the sealing performance. Processing is performed.
The pressing process is performed by a pressing apparatus using a pressing member 70 shown in FIG. The pressing member 70 is provided with a hemispherical surface 71 having a diameter substantially the same as that of the valve body at the tip. The pressing process is performed by bringing the hemispherical surface 71 into contact with the valve seat and pressing the valve seat with an appropriate load in the direction of the arrow 72. This reduces tolerances or minute irregularities that occur when the valve seat is formed by machining such as cutting and polishing.
Subsequently, the constant residual pressure valve is subjected to an oil tightness inspection between the valve body and the valve seat by an oil tightness inspection device. In this oil-tightness inspection, a valve body for oil-tightness inspection is attached to the inner passage of the relief valve, the inspection fluid is supplied to the inner passage on the upstream side of the valve seat, and the inspection fluid between the valve seat and the valve body is supplied. Detect the amount of leak.
In the oil tightness inspection, if the leak amount is within the specified value, the valve body, the spring that urges the valve body, and the adjuster pipe that adjusts the urging force of the spring are installed, and then combined with the relief valve to maintain the pressure. It is applied to the engine fuel supply system as a valve. On the other hand, if the amount of leak exceeds the standard value, it is installed again in the pressing device, and after pressing is performed, oil-tightness re-inspection is performed by the oil-tightness inspection device.

JP 2009-121395 A

However, after the oil-tightness inspection apparatus performs the oil-tightness inspection, if the pressing process is performed again by the pressing-processing apparatus, the manufacturing process becomes complicated, which delays the manufacturing time and increases the manufacturing cost. Concerned.
On the other hand, when a valve body, a spring and an adjuster pipe are attached to the product that has been subjected to the pressing process, and then an oil tightness inspection is performed, those whose leak amount exceeds the standard value will be installed in the pressing apparatus again and the pressing process will be performed. It becomes difficult.
The present invention has been made in view of the above problems, and an object of the present invention is to provide an inspection apparatus and an inspection method capable of shortening the time required for pressure holding valve pressing and oil tightness inspection and reducing manufacturing costs. It is to provide.
Another object of the present invention is to provide an inspection apparatus and an inspection method capable of reducing the equipment cost for manufacturing the pressure holding valve.

According to the first aspect of the present invention, there is provided a passage member having an inner passage through which a fluid can flow and a valve body that can be seated on and separated from a valve seat provided on the inner wall of the inner passage, and is located upstream of the valve seat. An inspection apparatus for inspecting the pressure holding performance of a pressure holding valve that holds the fuel pressure at a predetermined pressure includes a support, a pressing unit, a flow rate detecting unit, and a control unit. The support body supports the passage member, and the pressing means presses the valve body against the valve seat. The flow rate detecting means supplies a test fluid to the inner passage on the upstream side of the valve seat, and detects a leak amount of the test fluid between the valve seat and the valve body. When the detected value of the flow rate detection means exceeds the standard value, the control means drives the pressing means to press the valve body against the valve seat.
By pressing the valve body against the valve seat, the valve seat and the valve body are blended to improve the sealing performance, and the oil tightness inspection detects the amount of fluid leakage between the valve seat and the valve body. By using the same inspection device, the time required for the pressure holding valve to reciprocate between the pressing device and the oil tightness inspection device is shortened. Therefore, the manufacturing cost of the pressure holding valve can be reduced.
Further, since the pressing process can be performed in the inspection apparatus, the pressing apparatus that performs only the pressing process can be abolished, and the equipment cost for manufacturing the pressure holding valve can be reduced.
Furthermore, when the detection value of the flow rate detection means exceeds the standard value, readjustment can be performed by pressing in the inspection apparatus, so that the yield of the pressure holding valve can be increased.

According to the second aspect of the present invention, the pressure holding valve includes an urging means for urging the valve body toward the valve seat, and an urging force of the urging means provided in the inner passage on the opposite side of the valve seat of the urging means. It further has an adjuster pipe for adjusting. The pressing means is inserted through the urging means and the adjuster pipe, one end abuts against the valve body, a load is applied to the other end of the rod, and the valve body is pressed against the valve seat, and applied to the rod. Load detecting means for detecting the load to be applied.
If the load for pressing the valve body against the valve seat is increased, the valve seat and the valve body are brought into close contact with each other, and the familiarity is improved. However, if this load exceeds a certain value, the sealing surface between the valve seat and the valve body becomes wider, and the surface pressure of the sealing surface decreases, thereby increasing the amount of fuel leakage. For this reason, in the invention which concerns on Claim 2, it becomes possible for a load application means to press a valve body with a suitable load because a press means has a load detection means to detect the load applied to a rod. Therefore, the sealing performance between the valve seat and the valve body can be improved, and the yield of the pressure holding valve can be increased.

According to the third aspect of the invention, the inspection method for inspecting the pressure holding performance includes a support step for supporting the passage member, a first pressing step for pressing the valve body against the valve seat, and an upstream side of the valve seat. When the inspection fluid is supplied to the passage member and the leak value of the inspection fluid between the valve seat and the valve body is detected, and the detected value detected in the oil tightness inspection step exceeds the standard value, A second pressing process step of pressing the valve body again toward the valve seat.
As a result, when the sealing performance between the valve seat and the valve body is insufficient in the first pressing process, the sealing performance between the valve body and the valve seat is readjusted in the second pressing process, thereby shortening the work time. Thus, the manufacturing cost of the pressure holding valve is reduced. Further, the yield of the pressure holding valve can be increased.

The above-described pressure holding valve inspection device can be regarded as an invention of a pressing device that improves the sealing performance between the valve seat and the valve body of the pressure holding valve. Therefore, according to the invention according to claim 4, the pressing apparatus includes a support, a rod, a load application unit, and a load detection unit. The support supports the passage member. The rod passes through the biasing means and the adjuster pipe, and one end abuts on the valve body. The load applying means applies a load to the other end of the rod and presses the valve body against the valve seat. The load detection means detects a load applied to the rod.
Conventionally, as shown in FIG. 12, the pressure holding valve pressing device presses the valve seat using a pressing member 70 having a hemispherical surface 71 formed with a diameter substantially the same as that of the valve body. For this reason, after pressing the predetermined number of pressure holding valves, the pressing member 70 that has finished its life cycle has been replaced. In addition, pressing using the pressing member 70 near the end of the life cycle may make it difficult to reach the target accuracy.
In contrast, in the pressing device according to the fourth aspect of the present invention, the rod presses the valve element that is actually used for the pressure holding valve. For this reason, the conventional pressing member becomes unnecessary and manufacturing cost can be reduced. Furthermore, in the pressing device of the invention according to claim 4, since pressing is always performed with a new valve body, the processing accuracy of the pressing process is improved, and the sealing performance between the valve seat and the valve body can be improved.

It is sectional drawing of the inspection apparatus by 1st Embodiment of this invention. It is an enlarged view of the II part of FIG. 1, and is explanatory drawing which shows the state of a press process. It is a block diagram of the fuel supply system of the internal combustion engine provided with the pressure holding valve inspected by the inspection apparatus according to the first embodiment of the present invention. It is sectional drawing of the pressure holding valve which test | inspects with the test | inspection apparatus by 1st Embodiment of this invention. It is a characteristic view of the constant residual pressure valve of the pressure holding valve inspected by the inspection device according to the first embodiment of the present invention. It is a flowchart of the pressing process and oil-tightness inspection of the inspection apparatus by 1st Embodiment of this invention. It is a characteristic view which shows the relationship between the pressing load and the amount of fuel leaks in the pressing process of the pressure holding valve inspected by the inspection apparatus according to the first embodiment of the present invention. It is a flowchart of the manufacturing method of the pressure holding valve using the pressing apparatus by 2nd Embodiment of this invention. It is sectional drawing of the inspection apparatus by 3rd Embodiment of this invention. FIG. 10 is an enlarged view of a portion X in FIG. 9 and is an explanatory diagram illustrating a state of pressing. It is the elements on larger scale of the pressure holding valve which the test | inspection apparatus by 4th Embodiment of this invention inspects, and is explanatory drawing which shows the state of a press process. It is a top view of the press member used for the conventional pressing process.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
A first embodiment of the present invention is shown in FIGS.
First, the fuel supply system 1 of the engine in which the pressure holding valve 21 to be inspected by the inspection device 40 of the present embodiment will be described with reference to FIG. The fuel supply system 1 includes a fuel tank 2, a high-pressure pump 10, a delivery pipe 5, an injector 6, a pressure sensor 7, an engine control unit (ECU) 8, a pressure holding valve 21, and the like.

The fuel in the fuel tank 2 is pumped up by the low pressure pump 3 and supplied to the high pressure pump 10. This fuel is pressurized by the high-pressure pump 10, pumped through the high-pressure fuel pipe 4, and stored in the delivery pipe 5. The high-pressure fuel stored in the delivery pipe 5 is injected into each cylinder of the engine (not shown) by an injector 6 connected to the delivery pipe 5.
The pressure sensor 7 detects the fuel pressure in the delivery pipe 5 and transmits it to the ECU 8. The ECU 8 controls energization to the electromagnetic drive unit 13 of the high-pressure pump 10 to be described later based on detection values from the pressure sensor 7, an accelerator opening sensor (not shown), a rotation angle sensor (not shown) of the camshaft 9, and the like.

The high-pressure pump 10 includes a plunger 11, a suction valve 12, an electromagnetic drive unit 13, a discharge valve 14, and the like.
The plunger 11 is driven by the camshaft 9 of the engine and reciprocates in the axial direction. A pressurizing chamber 15 is formed on one end side of the plunger 11. The pressurizing chamber 15 has a variable volume by allowing the plunger 11 to reciprocate.
The suction valve 12 is provided in a supply passage 16 that connects the fuel inlet of the high-pressure pump 10 and the pressurizing chamber 15. The intake valve 12 is controlled to open and close the supply passage 16 by the operation of the electromagnetic drive unit 13.

  The discharge valve 14 is provided in a discharge passage 17 that connects the pressurizing chamber 15 and the fuel outlet of the high-pressure pump 10. In the discharge valve 14, the force that the valve body of the discharge valve 14 receives from the fuel on the pressurizing chamber 15 side causes the elastic force of the spring 18 that biases the valve body of the discharge valve 14 to the pressurizing chamber 15 side and the discharge valve 14. When the valve body becomes larger than the sum of the force received from the fuel on the delivery pipe 5 side, the discharge passage 17 is opened.

The operation of the high-pressure pump 10 is divided into an intake stroke, a return stroke, and a compression stroke.
In the suction stroke, the plunger 11 moves from the top dead center to the bottom dead center. At this time, energization to the electromagnetic drive unit 13 is stopped, and the suction valve 12 opens the supply passage 16. Due to the operation of the plunger 11, the pressure in the pressurizing chamber 15 decreases, and fuel is sucked into the pressurizing chamber 15 from the supply passage 16.
In the return stroke, the plunger 11 moves from the bottom dead center toward the top dead center. At this time, energization to the electromagnetic drive unit 13 is stopped, and the suction valve 12 opens the supply passage 16. Accordingly, the fuel in the pressurizing chamber 15 is discharged to the supply passage 16.
In the compression stroke, the electromagnetic drive unit 13 is energized while the plunger 11 is moving from the bottom dead center to the top dead center, and the suction valve 12 closes the supply passage 16. When the plunger 11 moves toward the top dead center in a state where the supply passage 16 is closed, the fuel pressure in the pressurizing chamber 15 increases. When the fuel pressure in the pressurizing chamber 15 exceeds a predetermined pressure, the discharge valve 14 opens the discharge passage 17. Thereby, high pressure fuel is discharged from the discharge passage 17 to the high pressure fuel pipe 4.

A return passage 20 is connected between the high-pressure fuel pipe 4 and the pressurizing chamber 15 of the high-pressure pump 10. A pressure holding valve 21 is provided in the return passage 20. The pressure holding valve 21 according to the present embodiment includes a relief valve 22 and a constant residual pressure valve 31.
As shown in FIG. 4, the relief valve 22 includes a relief valve body 23, a spring 24, a stopper 25, and the like.

The relief valve body 23 is formed in a substantially cylindrical shape, and an inner passage 30 is formed inside. The relief valve body 23 is provided with a conical valve seat 231 on the delivery pipe 5 side. The valve seat 231 can be seated on a valve seat 26 formed on the inner wall of the return passage 20. A chamfered portion 27 is formed on the radially outer wall of the relief valve body 23. Therefore, fuel can flow between the inner wall of the return passage 20 and the chamfered portion 27. Further, the relief valve body 23 is formed with a through hole 28 through the chamfered portion 27 and the inner wall of the inner passage 30 so that fuel can flow.
The stopper 25 is formed in a bottomed cylindrical shape, and is fixed to the inner wall of the return passage 20 on the side opposite to the valve seat 26 of the relief valve body 23. A hole 29 is provided at the bottom of the stopper 25 so that fuel can flow.
The spring 24 is a compression coil spring, one end of which is locked to the end of the relief valve body 23 opposite to the valve seat 26 and the other end of which is locked to the inner wall of the bottom of the stopper 25. The spring 24 presses the relief valve body 23 against the valve seat 26.

The constant residual pressure valve 31 is provided in the inner passage 30 of the relief valve body 23. The constant residual pressure valve 31 includes an orifice 32, a spherical valve body 33, a spring 34 as an urging means, and an adjuster pipe 35.
The orifice 32 is formed inside the diameter of the valve seat 231 of the relief valve body 23. A cylindrical portion 321 having an inner diameter larger than that of the orifice 32 is formed on the spherical valve body 33 side of the orifice 32.
A conical valve seat 36 is formed on the inner wall of the inner passage 30 by cutting and polishing. The spherical valve body 33 is accommodated in the inner passage 30 and can be seated on the valve seat 36. The spring 34 is a compression coil spring and is accommodated in the inner passage 30. The adjuster pipe 35 is formed in a cylindrical shape and is press-fitted into the inner wall of the inner passage 30. By adjusting the amount of press-fitting of the adjuster pipe 35, the urging force that the spring 34 presses the spherical valve element 33 against the valve seat 36 is set.

Next, the operation of the constant residual pressure valve 31 will be described with reference to FIG.
When the engine stops at time T1, the operation of the high-pressure pump stops with the rotation of the camshaft. If the fuel supply system does not include the constant residual pressure valve 31, the fuel pressure in the delivery pipe 5 maintains a high pressure as indicated by a broken line A. In this case, if the circulation of the cooling water in the engine is stopped and the fuel pressure in the delivery pipe 5 increases as the temperature of the engine room rises, there is a concern that fuel leaks from the injector 6 into the cylinder.

On the other hand, the constant residual pressure valve 31 reduces the fuel pressure of the delivery pipe 5 between the time T1 and the time T2, as indicated by the solid line B, after the engine stops at the time T1, and at a predetermined pressure after the time T2. Hold. Thereby, the fuel leakage amount of the injector 6 is suppressed within an allowable value.
If the pressure holding performance of the constant residual pressure valve 31 is lowered, the fuel pressure in the delivery pipe 5 may not be held at a predetermined pressure and may drop after time T2, as indicated by the broken line C. In this case, there is a concern that vapor is generated in the fuel, a pressure increase failure of the high pressure pump 10 occurs, and the engine start performance deteriorates.
Therefore, after the oil tightness inspection between the spherical valve element 33 and the valve seat 36 is performed, the constant residual pressure valve 31 is combined with the relief valve 22 only with a leak amount within the standard value, and the pressure holding valve 21 And is applied to the fuel supply system 1.

Next, the inspection apparatus 40 of this embodiment will be described with reference to FIG.
The inspection device 40 inspects the pressure retention performance of the constant residual pressure valve 31 constituting the pressure retention valve 21 by performing an oil tightness inspection and a pressing process between the spherical valve body 33 and the valve seat 36.
The inspection apparatus 40 includes an inspection case 41, a lid member 42, a support body 43, a pressing unit 44, a flow rate detection unit 45, a controller 46 as a control unit, and the like.
The inspection case 41 is formed in a bottomed cylindrical shape, and forms an accommodation space 411 in which the relief valve body 23 can be accommodated. In this embodiment, the relief valve body 23 corresponds to a “passage member” recited in the claims. A flange 412 is provided on the outer diameter side of the opening of the inspection case 41.
The lid member 42 contacts the flange 412 of the inspection case 41 and closes the opening of the inspection case 41. An O-ring 413 is provided between the inspection case 41 and the lid member 42 to ensure oil tightness.

The support body 43 includes a first support body 431 and a second support body 432, and supports the relief valve body 23 from both sides in the axial direction. The first support body 431 is formed integrally with the lid member 42. The first support 431 abuts on a shoulder 232 provided on the outer diameter side of the valve seat 231 of the relief valve body 23. An O-ring 433 is provided between the first support 431 and the shoulder 232 of the relief valve body 23 to ensure oil tightness.
The second support body 432 is formed of a material having elasticity, and is provided on the inner wall of the bottom portion of the inspection case 41. The second support body 432 presses the relief valve body 23 against the first support body 431.

The pressing unit 44 includes a rod 441, a load application unit (not shown), a load detection unit 442, and the like. The rod 441 is formed in a columnar shape, passes through a hole 414 provided in the bottom of the inspection case 41, passes through the adjuster pipe 35 and the spring 34 of the constant residual pressure valve 31, and one end is in contact with the spherical valve body 33. . One end of the rod 441 is formed in a hemispherical shape that is recessed in the axial direction, and is in surface contact with the spherical valve element 33. A packing 415 is provided between the hole 414 of the inspection case 41 and the rod 441 to ensure oil tightness.
The load applying means is constituted by an actuator, for example, and applies a load to the other end of the rod 441 as indicated by an arrow 443. Thereby, the spherical valve body 33 is pressed to the valve seat 36 side. The pressing load applied to the rod 441 is detected by a load detection unit 442 provided at the other end of the rod 441. The load detection means 442 outputs the detected value to the controller 46. The controller 46 controls the load application means and adjusts the pressing load.

The flow rate detection unit 45 includes a fluid supply unit (not shown), a flow rate detection sensor 451, and the like.
The fluid supply means supplies a test fluid to a test fluid inlet passage 421 formed in the lid member 42. The pressure of the inspection fluid supplied by the fluid supply means is set smaller than the valve opening pressure of the constant residual pressure valve 31. The inspection fluid may be a liquid or a gas.
The flow rate detection sensor 451 detects the amount of the inspection fluid flowing out from the inspection fluid outlet passage 416 provided at the bottom of the inspection case 41. The detection amount detected by the flow rate detection sensor 451 is output to the controller 46.
The controller 46 controls each part of the inspection apparatus 40 such as a load application unit and a fluid supply unit, and determines a leak amount from the detection value output from the flow rate detection sensor 451.

Next, a pressing process and an oil tightness inspection method performed by the inspection apparatus 40 will be described with reference to the flowchart shown in FIG. 6 and FIGS. 1, 2, and 7.
First, the relief valve body 23 is accommodated in the accommodation space 411 in the inspection case 41, and the end of the relief valve body 23 opposite to the shoulder 232 is brought into contact with the second support body 432. Subsequently, the opening of the inspection case 41 is closed by the lid member 42. At this time, the 1st support body 431 and the shoulder part 232 of the relief valve body 23 contact | abut. Thereby, the relief valve body 23 is supported by the first support body 431 and the second support body 432.

  Next, a first pressing process is performed by the pressing means 44 (S1). In the first pressing process, the load applying unit applies a load to the rod 441 as indicated by an arrow 443. As a result, the rod 441 presses the spherical valve element 33 against the valve seat 36. At this time, the load detection means 442 detects the pressing load applied to the rod 441 and outputs it to the controller 46. The controller 46 controls the driving of the load applying unit and adjusts the pressing load.

A state when the spherical valve body 33 is pressed against the valve seat 36 is shown in FIG.
The valve seat 36 may have minute irregularities formed by machining tolerance after machining such as cutting and polishing. In the present embodiment, a portion 361 that is recessed toward the inspection fluid inflow side is formed above the paper surface of FIG. 2, and a portion 362 that protrudes toward the inspection fluid outflow side is formed below the paper surface.
When the load applying means applies a load to the rod 441, the spherical valve element 33 moves as indicated by a broken line D, and a portion 362 below the paper surface of the valve seat 36 is plasticized toward the inspection fluid inflow side as indicated by a broken line E. Deform. Thereby, the spherical valve body 33 and the valve seat 36 become familiar, and the sealing performance is improved.

Here, the relationship between the pressing load applied to the rod 441 and the amount of fuel leak between the spherical valve element 33 and the valve seat 36 is shown in FIG.
As indicated by the solid line F, when the pressing load is smaller than P1, a minute gap remains between the spherical valve body 33 and the valve seat 36 due to insufficient conformity between the spherical valve body 33 and the valve seat 36, so that fuel leakage occurs. The amount increases. On the other hand, when the pressing load is larger than PX, the contact surface between the spherical valve element 33 and the valve seat 36 is widened, and the seal surface pressure is reduced, so that the amount of fuel leakage increases. Therefore, the pressing load has an optimum range of P1 to PX.
In the first pressing process, the pressing load applied by the load applying means to the rod 441 is set to P1 which is the minimum value in the optimum range. Thereby, after the constant residual pressure valve 31 is applied to the fuel supply system 1, a decrease in the seal surface pressure due to the gradual change of the spherical valve body 33 and the valve seat 36 is suppressed, and the durability of the constant residual pressure valve 31 is improved. improves.
Note that the relationship between the pressing load and the fuel leak amount may be as shown by a broken line G due to processing tolerances of the valve seat 36 or the valve body 31. Also in this case, the constant residual pressure valve 31 has a standard value and durability is improved by the following steps S2 to S4.

  After the controller 46 drives the load applying means and moves the rod 441 in the direction opposite to the arrow 443, an oil tightness inspection between the spherical valve element 33 and the valve seat 36 is performed by measuring the leak amount of the flow rate detecting means 45. (S2). In this oil tightness inspection, the fluid supply means supplies the inspection fluid to the inspection fluid inlet passage 421. The inspection fluid flows from the orifice 32 into the cylindrical portion 321. If a minute gap exists between the spherical valve element 33 and the valve seat 36, the inspection fluid flows into the inner passage 30 through the minute gap. The test fluid flows out from the test fluid outlet passage 416 through the through hole 28 and the accommodation space 411. The flow rate detection sensor 451 detects the flow amount of the inspection fluid and outputs it to the controller 46.

Next, the controller 46 detects the leak amount between the spherical valve element 33 and the valve seat 36 from the output value of the flow rate detection sensor 451, and determines whether or not this leak amount is within a standard value (S3). When the leak amount is within the standard value (S3: YES), the relief valve body 23 is taken out from the inspection case 41 as a product that has passed the oil tightness inspection, and the inspection ends.
On the other hand, when the leak amount exceeds the standard value (S3: NO), the controller drives the pressing means 44 to perform the second pressing process (S4). In the second pressing process, a pressing load P2 larger than the pressing load P1 of the first pressing process is set. However, the pressing load P2 is a load smaller than the maximum value PX in the optimum range. The pressing load P2 in the second pressing process is preferably a load smaller than an intermediate value between the minimum value P1 and the maximum value PX in the optimum range. Thereby, after applying the constant residual pressure valve 31 to the fuel supply system 1, the durability of the constant residual pressure valve 31 can be improved.

After the second pressing process is performed, the oil tightness inspection between the spherical valve element 33 and the valve seat 36 is performed again (S2). When the leak amount is within the standard value (S3: YES), the inspection is finished. On the other hand, when the leak amount exceeds the standard value (S3: NO), the second pressing process is performed again (S4). At this time, the controller 46 sets a pressing load P3 larger than the pressing load P2 set in the second pressing process. However, the pressing load P3 is a load smaller than the maximum value PX in the optimum range. The pressing load P3 is also preferably a load smaller than an intermediate value between the minimum value P1 and the maximum value PX.
After the second pressing process is performed again, the oil tightness inspection between the spherical valve element 33 and the valve seat 36 is performed again. If the leak amount is within the standard value (S3: YES), the oil tightness check is performed. The inspection ends with a pass. On the other hand, the controller 46 sets the product that has been subjected to the second pressing process a predetermined number of times as a product that has failed the oil tightness inspection, removes it from the inspection case 41, and ends the inspection. Alternatively, the pressing load of the second pressing process may be gradually increased, and the inspection may be terminated when the pressing load of the second pressing process becomes a certain value or more.

In the present embodiment, the pressing time (S1, S4) and the oil tightness inspection (S2) are performed by the same inspection device 40, so that the work time conventionally required to reciprocate between the pressing processing device and the oil tightness inspection device is as follows. This shortens the production efficiency. Therefore, the manufacturing cost of the constant residual pressure valve 31 can be reduced.
Moreover, since it becomes possible to perform pressing processing (S1, S4) in the inspection apparatus 40, the pressing processing apparatus which performs only pressing processing can be abolished, and the installation cost which manufactures the constant residual pressure valve 31 can be reduced. .
Furthermore, when the sealing performance between the spherical valve element 33 and the valve seat 36 does not satisfy the standard value in the first pressing process (S1), the sealing performance is readjusted in the second pressing process (S1). The yield of 31 can be raised.

(Second Embodiment)
The inspection device 40 according to the first embodiment described above can be regarded as a pressing device 40 that performs pressing processing between the spherical valve body 33 and the valve seat 36. A manufacturing method of the constant residual pressure valve 31 using the pressing device 40 is shown in FIG.
First, the valve seat 36 on which the spherical valve element 33 of the constant residual pressure valve 31 can be seated is formed by machining such as cutting and polishing in the inner passage 30 of the relief valve element 23 (S10).
Next, the spherical valve element 33 is accommodated in the inner passage 30 (S20).
Subsequently, the spring 34 is accommodated in the inner passage 30 (S30).
Next, the adjuster pipe 35 is press-fitted into the inner wall of the inner passage 30 to adjust the urging force of the spring 34 (S40).
Thereafter, the relief valve body 23 is installed in the pressing device 40. At this time, the relief valve body 23 is supported by the first support body 431 and the second support body 432, the rod 441 is inserted inside the adjuster pipe 35 and the spring 34, and one end of the rod 441 and the spherical valve body 33 are connected. Abut (S50).
Subsequently, a first pressing process is performed in which a load is applied to the other end of the rod 441 by the load applying means to press the spherical valve element 33 against the valve seat 36 (S60).
The steps S60 and S70 to S90 are substantially the same as the steps S1 to S4 of the first embodiment, and thus description thereof is omitted.

Here, a pressing member used in a conventional pressing apparatus is shown in FIG.
The pressing member 70 has a hemispherical surface 71 formed at the tip of the rod. In the conventional pressing device, after the valve seat 36 is formed in the inner passage 30 of the relief valve body 23, the pressing member 70 is inserted into the inner passage 30 to press the valve seat 36. For this reason, after pressing a certain number of constant residual pressure valves, the pressing member 70 that has finished its life cycle has been replaced. In addition, pressing using the pressing member 70 near the end of the life cycle may make it difficult to reach the target accuracy.

On the other hand, in this embodiment, when the constant residual pressure valve 31 is used in the fuel supply system 1, the rod 441 presses the spherical valve body 33 actually used for the constant residual pressure valve 31. For this reason, the conventional pressing member 70 becomes unnecessary, and the manufacturing cost can be reduced.
Furthermore, since pressing is always performed with the new spherical valve element 33, the accuracy of the pressing process is improved, and the sealing performance between the spherical valve element 33 and the valve seat 36 can be improved.

(Third embodiment)
An inspection device 40 according to a third embodiment of the present invention is shown in FIG. 9, and an enlarged view of a main part of the constant residual pressure valve 31 for performing the pressing process and the oil tightness inspection by the inspection device 40 is shown in FIG. 10. Components substantially the same as those of the first embodiment are denoted by the same reference numerals and description thereof is omitted.
The second support 433 of the inspection device 40 of the present embodiment is a coil spring, and the inspection fluid can flow in the radial direction.
Moreover, the needle valve 50 is used for the valve body of the constant residual pressure valve 31 which the inspection apparatus 40 of this embodiment performs a pressing process and an oil-tightness inspection.
The needle valve 50 has a large diameter cylindrical portion 51, a small diameter cylindrical portion 52, and a conical portion 53. A seal portion 54 is formed at a connection portion between the small diameter cylindrical portion 52 and the conical portion 53.
In the present embodiment, the seal portion 54 is in contact with a portion 364 below the paper surface of the valve seat 36 due to processing tolerances. On the other hand, a minute gap is formed between the seal portion 54 and a portion 363 above the paper surface of the valve seat 36.
When the inspection device 40 performs pressing, when the load applying means applies a load to the rod 441, the needle valve 50 moves as indicated by a broken line H, and a portion 364 below the paper surface of the valve seat 36 is indicated by a broken line I. Thus, it plastically deforms to the inspection fluid inflow side. Thereby, the needle valve 50 and the valve seat 36 become familiar, and the sealing performance is improved.

  In this embodiment, the needle valve 50 is used for the constant residual pressure valve 31 in which the inspection device 40 performs pressing processing and oil tightness inspection. The seal portion 54 of the needle valve 50 is in contact with the conical surfaces 363 and 364 of the valve seat 36. Even in such a shape, the load detection means 442 of the inspection device 40 applies an appropriate load required for plastic deformation of the conical surfaces 363 and 364 of the valve seat 6 to the needle valve 50. And the valve seat 36 can be blended to improve the sealing performance. Therefore, the same effect as the first and second embodiments described above can be obtained.

(Fourth embodiment)
FIG. 11 shows an enlarged view of the main part of a constant residual pressure valve in which the inspection apparatus according to the fourth embodiment of the present invention performs pressing and oil tightness inspection.
The needle valve 60 of the constant residual pressure valve 31 in which the inspection apparatus of the present embodiment performs pressing and oil tightness inspection has a large diameter cylindrical portion 61, a small diameter cylindrical portion 62, and a conical portion 63. In the needle valve 60 of the present embodiment, the conical portion 63 becomes the seal portion 64.
Even if the needle valve 60 has such a shape, the load detection means of the inspection apparatus applies a load appropriate for plastic deformation of the valve seat 362 to the rod 441, so that the needle valve 50 and the valve seats 361 and 362 are connected. Familiarity and sealability can be improved. Therefore, the same operational effects as those of the first to third embodiments described above can be achieved.

(Other embodiments)
In the above-described embodiments, the inspection device or the pressing device for the pressure holding valve 21 in which the relief valve 22 and the constant residual pressure valve 31 are integrally configured have been described. On the other hand, the present invention is an inspection device or a pressing device used for a pressure holding valve in which a relief valve, a constant residual pressure valve are separately formed, or a pressure holding valve other than the above used in a fuel supply system. May be.
In the above-described embodiments, the pressing process and the oil tightness inspection are alternately performed. On the other hand, the present invention may perform the pressing process and the oil tightness inspection at the same time. That is, the load application means moves the rod in the pressing process, and the load is applied to the valve seat and the valve body, and at the same time, the flow rate detection means performs the oil tightness inspection, thereby shortening the work time. Moreover, a load suitable for each pressure holding valve can be applied.
Thus, the present invention is not limited to the above-described embodiments, and can be implemented in various forms without departing from the spirit of the invention.

  22: Relief valve (pressure holding valve), 23: Relief valve body (passage member), 31: Constant residual pressure valve (pressure holding valve), 33: Spherical valve body (valve body), 36: Valve seat, 40: Inspection device , 43: support, 44: pressing means, 45: flow rate detection means, 46: controller (control means), 431: first support (support), 432: second support (support), 441: rod (Pressing means), 442: Load detecting means (Pressing means), 451: Flow rate detecting sensor (Flow rate detecting means)

Claims (4)

A passage member provided in a fuel supply system of an internal combustion engine, having a passage member having an inner passage through which fuel can be circulated, and a valve body seated on and separated from a valve seat provided on an inner wall of the inner passage, An inspection device for inspecting the pressure holding performance of a pressure holding valve that holds an upstream fuel pressure at a predetermined pressure,
A support for supporting the passage member;
Pressing means for pressing the valve body against the valve seat;
A flow rate detecting means for supplying a test fluid to the inner passage on the upstream side of the valve seat and detecting a leak amount of the test fluid between the valve seat and the valve body;
And a control means for driving the pressing means to press the valve body against the valve seat when the detection value of the flow rate detection means exceeds a standard value. The pressure holding valve is provided in an urging means for urging the valve body toward the valve seat, and the inner passage on the opposite side of the urging means from the valve seat, and adjusts the urging force of the urging means. And an adjuster pipe to be
The pressing means is inserted through the biasing means and the adjuster pipe, and a rod whose one end is in contact with the valve body;
A load applying means for applying a load to the other end of the rod and pressing the valve body against the valve seat;
The pressure holding valve inspection device according to claim 1, further comprising a load detection unit configured to detect a load applied to the rod. A passage member provided in a fuel supply system of an internal combustion engine, having a passage member having an inner passage through which fuel can be circulated, and a valve body seated on and separated from a valve seat provided on an inner wall of the inner passage, An inspection method for inspecting the pressure holding performance of a pressure holding valve that holds the upstream fuel pressure at a predetermined pressure,
A supporting step for supporting the passage member;
A first pressing process for pressing the valve body against the valve seat;
An oil tightness inspection step of supplying a test fluid to the inner passage on the upstream side of the valve seat and detecting a leak amount of the test fluid between the valve seat and the valve body;
And a second pressing process step of pressing the valve body again to the valve seat side when the detection value detected in the oil tightness inspection step exceeds a standard value. Method. A passage member having an inner passage through which fuel can flow, a valve body that can be seated and separated from a valve seat provided on an inner wall of the inner passage, a biasing means that biases the valve seat toward the valve seat, and A pressing device for improving the sealing performance between the valve seat and the valve body of the pressure holding valve provided in the inner passage on the opposite side of the valve body of the urging means and having an adjuster pipe for setting the urging force of the urging means Because
A support for supporting the passage member;
A rod that is inserted through the biasing means and the adjuster pipe and has one end abutting the valve body;
A load applying means for applying a load to the other end of the rod and pressing the valve body against the valve seat;
A pressing apparatus comprising load detecting means for detecting a load applied to the rod.

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