WO2013027528A1 - 電磁ポンプ装置 - Google Patents
電磁ポンプ装置 Download PDFInfo
- Publication number
- WO2013027528A1 WO2013027528A1 PCT/JP2012/068833 JP2012068833W WO2013027528A1 WO 2013027528 A1 WO2013027528 A1 WO 2013027528A1 JP 2012068833 W JP2012068833 W JP 2012068833W WO 2013027528 A1 WO2013027528 A1 WO 2013027528A1
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- WIPO (PCT)
- Prior art keywords
- diameter
- check valve
- electromagnetic pump
- pump device
- reduced
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/1002—Ball valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
- F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
- F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
- F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
- F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
- F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
- F04B17/044—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow using solenoids directly actuating the piston
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on pistons
- F04B53/125—Reciprocating valves
- F04B53/126—Ball valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/20—Filtering
Definitions
- the present invention relates to an electromagnetic pump device in which a strainer is attached to a suction port.
- this type of electromagnetic pump device includes an electromagnetic part, a movable iron core that can reciprocate in the pump chamber in the axial direction by turning the electromagnetic part on and off, and a one-way direction from the suction port to the pump chamber. Proposed is provided with an inlet check valve mechanism that allows the flow of hydraulic oil and an outlet check valve mechanism that is built in the pump chamber and allows a one-way flow of hydraulic oil from the pump chamber to the discharge port (For example, refer to Patent Document 1).
- the suction port extends in the axial direction from the inlet check valve mechanism and then opens in a direction perpendicular to the axial direction to be connected to the oil passage.
- a strainer is installed. Further, in order to reduce the inflow resistance of the hydraulic oil flowing into the strainer, the step portion is formed so that the connection portion with the oil passage has a diameter one step larger than that of the suction port.
- the main purpose of the electromagnetic pump device of the present invention is to have a compact configuration while allowing smooth suction of the working fluid.
- the electromagnetic pump device of the present invention employs the following means in order to achieve the above-mentioned main object.
- the electromagnetic pump device of the present invention is A through hole that has a cylindrical portion and a flange portion that extends in a radial direction from an edge of the cylindrical portion and penetrates the cylindrical portion and the flange portion to form an inlet at the end surface of the flange portion is formed.
- a check valve for inhalation A strainer attached to the suction port and having a pore forming region in which a large number of pores are formed in an area larger than an inner diameter of the cylindrical portion of the through hole; With The suction check valve is formed with a reduced diameter portion so that the diameter of the through hole is reduced from the flange portion toward the cylindrical portion with a degree of reduction in diameter that changes from large to small.
- the gist is formed with a reduced diameter portion so that the diameter of the through hole is reduced from the flange portion toward the cylindrical portion with a degree of reduction in diameter that changes from large to small.
- the electromagnetic pump device has a tubular portion and a flange portion extending in a radial direction from an edge of the tubular portion, and penetrates the tubular portion and the flange portion to form an inlet at the end surface of the flange portion.
- a suction check valve having a through hole is provided, and the check valve for suction is reduced in diameter so that the inner diameter of the through hole changes from large to small from the flange portion toward the cylindrical portion.
- a reduced diameter portion is formed.
- the reduced diameter portion may be formed by two stages of tapered surfaces having different inclination angles. In this way, the reduced diameter portion can be formed by a relatively simple process.
- the reduced diameter portion has an inflection point at which an inclination angle of the two-step tapered surface changes, and a thickness of a boundary portion between the cylindrical portion and the flange portion is predetermined. It can also be determined at a position that is equal to or greater than the thickness. If it carries out like this, the thickness of the boundary part of a flange part and a cylindrical part can be ensured more reliably.
- the suction check valve has a straight portion formed between the end face of the flange portion and the reduced diameter portion so as to have a uniform diameter with the inner diameter of the suction port. It can also be. In this way, the working fluid can be sucked more smoothly. Moreover, since the area of the end surface of the flange part covered with a strainer can be made comparatively large, the pressure of the working fluid which acts on a strainer can be received more appropriately.
- the suction check valve may be formed such that the inner diameter of the suction port is larger than the outer diameter of the cylindrical portion.
- the suction check valve when the diameter is reduced from the second inner diameter toward the first inner diameter at a certain degree, a portion where the thickness is largely reduced is likely to be generated. Therefore, it is significant to apply the present invention.
- the suction check valve may be built in the cylinder. If it carries out like this, an electromagnetic pump apparatus can be made into a more compact structure.
- FIG. 7 is a perspective view of a plug 78.
- FIG. FIG. 5 is a cross-sectional view taken along the line AA in the perspective view of the plug 78 in FIG.
- FIG. 5 shows the comparative example at the time of forming the reduced diameter part different from an Example.
- FIG. 5 shows a mode that the check valve 80 for discharge is assembled
- FIG. 3 is an explanatory view showing a state in which a piston 60, a discharge check valve 80, a spring 46, a suction check valve 70, and a strainer 90 are assembled to a cylinder 50.
- FIG. 1 is a block diagram showing an outline of the configuration of an electromagnetic pump 20 as an embodiment of the present invention.
- the electromagnetic pump 20 according to the embodiment includes a solenoid unit 30 that generates an electromagnetic force, and a pump unit 40 that operates by the electromagnetic force of the solenoid unit 30.
- the electromagnetic pump 20 is configured as a part of a hydraulic control device for hydraulically driving a friction engagement element (clutch or brake) included in the automatic transmission, for example, in a vehicle equipped with an engine and an automatic transmission. be able to.
- a friction engagement element clutch or brake
- an electromagnetic coil 32, a plunger 34 as a mover, and a core 36 as a stator are arranged in a solenoid case 31 as a bottomed cylindrical member.
- the solenoid unit 30 forms a magnetic circuit in which a magnetic flux circulates around the solenoid case 31, the plunger 34, and the core 36 by applying a current to the electromagnetic coil 32, and the shaft that is attracted to the plunger 34 and abuts on the tip of the plunger 34.
- Extrude 38 Extrude 38.
- the pump unit 40 is configured as a piston pump that pumps hydraulic oil by reciprocating the piston 60 by the electromagnetic force from the solenoid unit 30 and the biasing force of the spring 46, and one end of the pump unit 40 is a solenoid case 31 of the solenoid unit 30.
- a spring 46 that urges the piston 60 in a direction opposite to the direction in which the electromagnetic force from the contact solenoid part 30 acts, and a direction in which the spring 46 is supported from the side opposite to the front end surface of the piston 60 and sucked into the pump chamber 56.
- An intake check valve 70 that permits the flow of hydraulic oil and prohibits a reverse flow, and an intake port of the intake check valve 70 are provided.
- a strainer 90 that captures foreign matters such as dust contained in the hydraulic fluid that is introduced, and a discharge check that permits the flow of hydraulic fluid that is built in the piston 60 and discharges from the pump chamber 56 and prohibits the reverse flow.
- a cylinder cover 48 that covers the other end of the cylinder 50 in a state where the piston 60, the discharge check valve 80, the spring 46, and the suction check valve 70 are disposed in the cylinder 50.
- the pump portion 40 is formed such that a suction port 42 is formed at the center of the cylinder cover 48 and a discharge port 44 is formed by cutting out a part in the circumferential direction on the side surface of the cylinder 50.
- the piston 60 has a stepped shape including a cylindrical piston main body 62 and a cylindrical shaft portion 64 having an outer diameter smaller than that of the piston main body 62 and having an end surface in contact with the tip of the shaft 38 of the solenoid portion 30. It is formed and reciprocates in the cylinder 50 in conjunction with the shaft 38 of the solenoid unit 30.
- the piston 60 is formed with a cylindrical bottomed hollow portion 62a at the center of the shaft, and a discharge check valve 80 is disposed in the hollow portion 62a. Further, the hollow portion 62 a extends from the front end surface of the piston 60 through the inside of the piston main body 62 to the middle of the inside of the shaft portion 64.
- the shaft portion 64 is formed with two through holes 64a and 64b that intersect each other at an angle of 90 degrees in the radial direction.
- a discharge port 44 is formed around the shaft portion 64, and the hollow portion 62a communicates with the discharge port 44 through two through holes 64a and 64b.
- the suction check valve 70 is inserted into the cylinder 50 and has a hollow portion 72a with a bottom formed therein, and a center that connects the hollow portion 72a and the pump chamber 56 at the center of the shaft to the bottom of the hollow portion 72a.
- biasing force to the ball 74, and the plug 78 which makes the seat part of the ball 74 are provided.
- FIG. 2 shows how the intake check valve 70 is assembled
- FIG. 3 shows the appearance after the intake check valve 70 is assembled.
- the suction check valve 70 is inserted by inserting a spring 76 and a ball 74 into the hollow portion 72a of the valve body 72 in this order, and then press-fitting a plug 78 into the hollow portion 72a.
- the plug 78 is a cylindrical member with a flange having a cylindrical portion 78a having an outer diameter capable of being press-fitted into the hollow portion 72a of the valve main body 72, and a flange portion 78b extending in a radial direction from an end edge of the cylindrical portion 78a.
- the strainer 90 is attached so as to cover the end surface of the flange portion 78b. As shown in FIG.
- the strainer 90 has a disk portion 92 having a large number of pores formed in the center region (pore formation region 92 a) and forms a strainer surface, and extends in an orthogonal direction from the outer peripheral edge of the disk portion 92.
- the claw at the tip is composed of three leg portions 94 bent inward. Therefore, as shown in FIG. 3, when the strainer 90 is put on the flange portion 78b of the plug 78 from the leg portion 94, the claw at the tip of the leg portion 94 is caught on the stepped portion between the flange portion 78b and the cylindrical portion 78a. , Not to fall out.
- the intake check valve 70 and the strainer 90 are assembled in this manner, thereby making them sub-assies (see FIG. 3).
- FIG. 4 is a perspective view of the plug 78
- FIG. 5 is a cross-sectional view taken along the line AA in the perspective view of the plug 78 of FIG.
- the plug 78 is formed with a through hole 78c penetrating the cylindrical portion 78a and the flange portion 78b.
- the cylindrical portion 78a has an inner diameter D1 smaller than the outer diameter of the ball 74 and a length L.
- the center part 79 is formed.
- the inner diameter D1 is obtained, for example, by determining the flow rate of the hydraulic oil that passes through the central portion 79 from the discharge amount (intake amount) required for the electromagnetic pump 20, and the calculated flow rate and the hydraulic fluid that passes through the central portion 79. It is determined based on the flow velocity and inflow resistance. Further, the plug 78 is formed with a tapered portion 79a that communicates with the central portion 79 and gradually increases in inner diameter from the left to the right in FIG. 5, and the ball 74 comes into contact with the tapered portion 79a. Is positioned.
- a straight portion 79b having an inner diameter D2 equivalent to the diameter of the pore forming region 92a of the strainer 90 over a predetermined length is formed on the plug 78 on the end surface 78b1 side of the flange portion 78b.
- the size and number of pores of the strainer 90 are obtained by determining the size of the pores in consideration of, for example, the size of foreign matter to be trapped, the flow rate of hydraulic oil passing through the pores, the inflow resistance, and the like. Is calculated by calculating the number of pores so that the required flow rate of hydraulic fluid can be sucked on the basis of the above-described size and the flow rate of the central portion 79 described above.
- the diameter that is, the inner diameter D2 of the pore forming region 92a is determined from the size and number of the pores thus obtained.
- the inner diameter D2 is determined to be larger than the outer diameter of the cylindrical portion 78a.
- the plug 78 has a reduced diameter portion 79c that gradually decreases in inner diameter from the flange portion 78b side toward the cylindrical portion 78a side (from the left to the right in FIG. 5).
- the reduced diameter portion 79c has two-step tapered surfaces 79c1 and 79c2 having different surface inclination angles with respect to the axial center of the central portion 79, and the inclination angle (angle ⁇ in FIG. 5) of the tapered surface 79c2 is tapered.
- FIG. 6 shows a comparative example in which a reduced diameter portion different from the embodiment is formed.
- FIG. 6A shows a comparative example 1 in which a tapered surface having an inclination angle ⁇ (an inclination angle of the tapered surface 79c1) is formed from the inner diameter D1 of the central portion 79 to the inner diameter D2 of the straight portion 79b.
- ⁇ an inclination angle of the tapered surface 79c1
- the thickness T of the boundary portion between the cylindrical portion 78a and the flange portion 78b is remarkably reduced as compared with the embodiment, and thus the rigidity of the plug 78 may be insufficient.
- the thickness T tends to be thin.
- FIG. 6B shows a comparative example 2 in which a tapered surface having an inclination angle ⁇ is formed from the inner diameter D2 of the straight portion 79b to the inner diameter D1 of the central portion 79 so as to maintain the thickness T at the same thickness as the embodiment.
- FIG. 6C shows a comparative example 3 in which a tapered surface having an inclination angle ⁇ (an inclination angle of the tapered surface 79c2) is formed from the inner diameter D1 of the central portion 79 to the inner diameter D2 of the straight portion 79b.
- the thickness of the flange portion 78b increases and the plug 78 becomes larger than the embodiment. For this reason, the check valve 70 for suction also becomes large, leading to an increase in the size of the electromagnetic pump 20.
- the thickness T of the plug 78 is insufficient, resulting in insufficient rigidity, or the length L of the central portion 79 is increased.
- the smooth flow of hydraulic oil may be hindered, or the thickness of the flange portion 78b may increase, leading to an increase in the size of the intake check valve 70 (electromagnetic pump 20).
- the taper surface 79c2 with a small degree of diameter reduction makes the thickness T sufficient, and the taper surface 79c1 with a large degree of diameter reduction suppresses an increase in the thickness of the flange portion 78b while reducing the inner diameter. Is expanded to the inner diameter D2. Further, since the diameter-reduced portion 79c is gradually reduced in diameter from the flange portion 78b side toward the cylindrical portion 78a side, the hydraulic oil can be sucked smoothly. Accordingly, the plug 78 can be prevented from becoming large while ensuring the rigidity of the plug 78, and the working oil can be sucked smoothly. For this reason, the diameter-reduced portion 79c is reduced with a degree of diameter reduction in which the inner diameter of the through hole 78c of the plug 78 changes from the inner diameter D2 to the inner diameter D1.
- such a reduced diameter portion 79c is realized by providing the two-step tapered surfaces 79c1 and 79c2, and therefore can be formed relatively easily without requiring complicated processing.
- the inflection point P (see FIG. 5) where the inclination angle of the two-step tapered surfaces 79c1 and 79c2 changes is set such that the thickness T of the boundary portion between the cylindrical portion 78a and the flange portion 78b is equal to or larger than a predetermined thickness.
- the flange portion 78b is determined at a position where it can be made as thin as possible. For this reason, the thickness of the flange 78b can be suppressed while ensuring the thickness T of the plug 78 more reliably.
- the predetermined thickness can be set to a thickness that can ensure the rigidity and durability required for the plug 78 in consideration of, for example, the pressure and flow rate of the hydraulic oil sucked through the strainer 90. Further, since the straight portion 79b is formed between the end surface 78b1 of the flange portion 78b and the reduced diameter portion 79c, the hydraulic oil can flow smoothly compared to the case where the tapered surface is connected to the end surface 78b1. In addition, the annular area of the end surface 78b1 can be increased to more appropriately receive the pressure of the hydraulic oil acting on the cylinder cover 48 and the strainer 90.
- the end surface 78b1 covered by the strainer 90 functions as a pressure receiving surface that receives the pressure of the hydraulic oil acting on the cylinder cover 48 and the strainer 90. Therefore, when the area is increased, the strainer 90 and the flange portion 78b (plug 78). ) Can be prevented from acting too much stress.
- the intake check valve 70 74 When the differential pressure (P1-P2) between the pressure P1 on the input side and the pressure P2 on the output side is equal to or higher than a predetermined pressure that overcomes the urging force of the spring 76, the intake check valve 70 74 is opened by being separated from the plug 78, and when the above-described differential pressure (P1-P2) is less than a predetermined pressure, the ball 74 is pressed against the taper portion 79a of the plug 78 with the extension of the spring 76 and penetrates. The valve 78 is closed by closing the hole 78c.
- the soot discharge check valve 80 includes a ball 84, a spring 86 that applies a biasing force to the ball 84, and a plug 88 as an annular member having a center hole 89 having an inner diameter smaller than the outer diameter of the ball 84.
- FIG. 7 shows how the discharge check valve 80 is assembled
- FIG. 8 shows the appearance after the discharge check valve 80 is assembled to the piston 60.
- the discharge check valve 80 is inserted by inserting a spring 86 and a ball 84 into the hollow portion 62a of the piston 60 in this order, and then press-fitting a plug 88 into the hollow portion 62a.
- the plug 88 can be fixed to the piston 60 by a fixing member such as a snap ring. In the embodiment, by assembling the discharge check valve 80 to the piston 60 in this way, these are used as sub-assies (see FIG. 8).
- the discharge check valve 80 has a predetermined pressure (P2-P3) between the pressure on the input side (the pressure on the output side of the check valve 70 for suction) P2 and the pressure P3 on the output side to overcome the biasing force of the spring 86.
- P2-P3 a predetermined pressure
- the ball 84 is released from the center hole 89 of the plug 88 with the contraction of the spring 86, and when the pressure difference (P2-P3) is less than the predetermined pressure, the spring 86 is expanded.
- the ball 84 is pressed against the central hole 89 of the plug 88 to close the central hole 89, the valve is closed.
- the soot cylinder 50 forms a pump chamber 56 by a space surrounded by the inner wall 51, the front end surface of the piston 60 and the surface of the suction check valve 70 on the spring 46 side.
- the suction check valve 70 is opened and the discharge check valve 80 is closed as the volume in the pump chamber 56 increases.
- the suction check valve 70 is closed and the discharge reverse valve is closed as the volume in the pump chamber 56 is reduced.
- the stop valve 80 opens to discharge the hydraulic oil sucked through the discharge port 44.
- an inner wall 52 on which the piston main body 62 slides and an inner wall 54 on which the shaft portion 64 slides are formed with a step, and the discharge port 44 is formed at the step portion.
- the step portion forms a space surrounded by the annular surface of the step portion between the piston main body 62 and the shaft portion 64 and the outer peripheral surface of the shaft portion 64. Since this space is formed on the opposite side of the pump chamber 56 across the piston main body 62, the volume decreases when the volume of the pump chamber 56 increases, and the volume decreases when the volume of the pump chamber 56 decreases. Expanding.
- the volume change of this space is such that the area (pressure receiving area) that receives pressure from the pump chamber 56 side of the piston 60 is larger than the area (pressure receiving area) that receives pressure from the discharge port 44 side. It becomes smaller than the volume change. For this reason, this space functions as the second pump chamber 58. That is, when the piston 60 is moved by the urging force of the spring 46, an amount of hydraulic oil corresponding to the enlarged volume of the pump chamber 56 is sucked into the pump chamber 56 from the suction port 42 via the suction check valve 70.
- FIG. 9 is an explanatory view showing the state of assembly of the electromagnetic pump 20 of the embodiment.
- the assembly of the electromagnetic pump 20 of the embodiment includes the subassembly of the piston 60 and the discharge check valve 80, the spring 46, the subassembly of the intake check valve 70 and the strainer 90. Inserting in this order, and then attaching the cylinder cover 48.
- the outer peripheral surface of the cylinder 50 and the inner peripheral surface of the cylinder cover 48 are each engraved with a spiral groove (not shown).
- the cylinder cover 48 is attached by screwing the cylinder cover 48 over the cylinder 50. Done.
- the outer peripheral edge of the strainer 90 is pressed by the annular pressing surface 48a of the cylinder cover 48, and the strainer 90 is fixed.
- the suction check valve 70 has a degree of diameter reduction in which the inner diameter of the through-hole 78c changes from large to small from the flange portion 78b of the plug 78 toward the cylindrical portion 78a. Therefore, the thickness of the boundary portion between the flange portion 78b and the cylindrical portion 78a is suppressed while suppressing an increase in the thickness of the flange portion 78b as compared with a portion having a constant diameter reduction. T can be secured, and the hydraulic oil can be sucked smoothly by the reduced diameter of the reduced diameter portion 79c. As a result, it is possible to prevent the suction check valve 70 from becoming large while enabling smooth suction of the hydraulic oil, and the electromagnetic pump 20 can be made compact.
- the reduced diameter portion 79c is formed by the two-step tapered surfaces 79c1 and 79c2, it can be formed by relatively easy processing. Furthermore, since the inflection point P of the inclination angle of the two-step tapered surfaces 79c1 and 79c2 is determined within a range where the thickness T of the boundary portion between the cylindrical portion 78a and the flange portion 78b is equal to or greater than a predetermined thickness, the thickness T is It can be ensured more reliably. Since the straight portion 79b is formed between the end surface 78b1 of the flange portion 78b and the reduced diameter portion 79c, the working oil can be sucked more smoothly, and the working oil acting on the strainer 90 at the end surface 78b1. The pressure can be received more appropriately. Further, since the suction check valve 70 is built in the cylinder 50, the electromagnetic pump 20 can be made more compact.
- the reduced diameter portion 79c of the plug 78 of the suction check valve 70 is composed of the two-stage tapered surfaces 79c1 and 79c2, but is composed of two or more stages of tapered surfaces.
- the step surface is not limited to the tapered surface, and may be a stepped surface having a plurality of steps or a curved surface having an R-shaped cross section.
- the inner diameter D2 is equal to the diameter of the pore forming region 92a of the strainer 90 and is larger than the outer diameter of the cylindrical portion 78a. A smaller inner diameter may be used.
- the straight portion 79b is formed in the plug 78 of the suction check valve 70, but it may not be formed.
- the suction check valve 70 is built in the cylinder 50, but the suction check valve may be built in a valve body outside the cylinder 50 and not built in the cylinder 50.
- the suction port connected to the pump chamber is formed by closing the opening of the cylinder 50 where the check valve 70 is disposed, and the end surface 78b1 of the plug 78 of the check valve 70 is covered.
- the strainer 90 is fixedly attached to the flange portion 78b, and the suction port of the pump chamber of the cylinder 50 and the output port of the suction check valve 70 (corresponding to the center hole 72b in the embodiment) are connected by an oil passage. What is necessary is just to comprise.
- the electromagnetic pump 20 of the embodiment is configured as an electromagnetic pump of a type that discharges hydraulic oil twice from the discharge port 44 by one reciprocating motion of the piston 60.
- the present invention is not limited to this.
- the hydraulic oil When the piston is moved forward by electromagnetic force from the part, the hydraulic oil is sucked into the pump chamber from the suction port, and when the piston is moved backward by the biasing force of the spring, the hydraulic oil in the pump chamber is discharged from the discharge port.
- the hydraulic oil is drawn into the pump chamber from the suction port, and the hydraulic oil in the pump chamber is discharged from the discharge port when the piston is moved forward by the electromagnetic force from the solenoid section
- any type of electromagnetic pump may be used.
- the electromagnetic pump 20 of the embodiment is used for a hydraulic control device for hydraulically driving clutches and brakes of an automatic transmission mounted on an automobile.
- the invention is not limited to this.
- fuel is transferred or lubricated.
- the present invention may be applied to any system such as transferring a liquid for use.
- the strainer 90 corresponds to the “strainer”
- the cylindrical portion 78a of the plug 78 corresponds to the “tubular portion”
- the flange portion 78b corresponds to the “flange portion”
- the through hole 78c becomes the “through hole”.
- the suction check valve 70 corresponds to the “suction check valve”
- the reduced diameter portion 79c corresponds to the “reduced diameter portion”.
- the present invention can be used in the manufacturing industry of electromagnetic pump devices.
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Abstract
Description
筒部と、該筒部の端縁から径方向に延伸されるフランジ部とを有し、前記筒部と前記フランジ部とを貫通して該フランジ部の端面で吸入口をなす貫通孔が形成された吸入用逆止弁と、
前記吸入口に取り付けられ、前記貫通孔の前記筒部における内径よりも大きな領域であって多数の細孔が形成された細孔形成領域を有するストレーナと、
を備え、
前記吸入用逆止弁は、前記フランジ部から前記筒部に向かって前記貫通孔の内径が大から小に変化する縮径の度合いをもって縮径されるよう縮径部が形成されてなる
ことを要旨とする。
Claims (6)
- 筒部と、該筒部の端縁から径方向に延伸されるフランジ部とを有し、前記筒部と前記フランジ部とを貫通して該フランジ部の端面で吸入口をなす貫通孔が形成された吸入用逆止弁と、
前記吸入口に取り付けられ、前記貫通孔の前記筒部における内径よりも大きな領域であって多数の細孔が形成された細孔形成領域を有するストレーナと、
を備え、
前記吸入用逆止弁は、前記フランジ部から前記筒部に向かって前記貫通孔の内径が大から小に変化する縮径の度合いをもって縮径されるよう縮径部が形成されてなる
ことを特徴とする電磁ポンプ装置。 - 前記縮径部は、傾斜角の異なる二段のテーパ面により形成されてなる請求項1記載の電磁ポンプ装置。
- 前記縮径部は、前記二段のテーパ面の傾斜角が変化する変曲点が、前記筒部と前記フランジ部との境界部分の厚みが所定の厚み以上となる位置に定められてなる請求項2記載の電磁ポンプ装置。
- 前記吸入用逆止弁は、前記フランジ部の端面と前記縮径部との間に、前記吸入口の内径をもって均一の径に形成されたストレート部を有する請求項1ないし3いずれか1項に記載の電磁ポンプ装置。
- 前記吸入用逆止弁は、前記吸入口の内径が前記筒部の外径よりも大きな径に形成されてなる請求項1ないし4いずれか1項に記載の電磁ポンプ装置。
- シリンダ内をピストンが往復動することにより作動流体を圧送する請求項1ないし5いずれか1項に記載の電磁ポンプ装置であって、
前記吸入用逆止弁は、前記シリンダに内蔵されてなる電磁ポンプ装置。
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DE112012002449.4T DE112012002449B4 (de) | 2011-08-24 | 2012-07-25 | Elektromagnetische Pumpvorrichtung mit Ansaugrückschlagventil |
US14/124,467 US9429154B2 (en) | 2011-08-24 | 2012-07-25 | Electromagnetic pump device |
CN201280034236.6A CN103649537B (zh) | 2011-08-24 | 2012-07-25 | 电磁泵装置 |
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JP2011183147A JP5505386B2 (ja) | 2011-08-24 | 2011-08-24 | 電磁ポンプ装置 |
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JP (1) | JP5505386B2 (ja) |
CN (1) | CN103649537B (ja) |
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WO2015023804A1 (en) | 2013-08-13 | 2015-02-19 | Polyera Corporation | Optimization of electronic display areas |
CN105793781B (zh) | 2013-08-27 | 2019-11-05 | 飞利斯有限公司 | 具有可挠曲电子构件的可附接装置 |
WO2015031426A1 (en) | 2013-08-27 | 2015-03-05 | Polyera Corporation | Flexible display and detection of flex state |
WO2015038684A1 (en) | 2013-09-10 | 2015-03-19 | Polyera Corporation | Attachable article with signaling, split display and messaging features |
KR101584862B1 (ko) | 2013-12-04 | 2016-01-12 | 이종열 | 왕복 펌프 및 이를 이용한 샘플러 |
WO2015100404A1 (en) | 2013-12-24 | 2015-07-02 | Polyera Corporation | Support structures for a flexible electronic component |
CN106030687B (zh) | 2013-12-24 | 2020-08-14 | 飞利斯有限公司 | 动态可挠物品 |
EP3087812B9 (en) | 2013-12-24 | 2021-06-09 | Flexterra, Inc. | Support structures for an attachable, two-dimensional flexible electronic device |
WO2015100224A1 (en) | 2013-12-24 | 2015-07-02 | Polyera Corporation | Flexible electronic display with user interface based on sensed movements |
US20150227245A1 (en) | 2014-02-10 | 2015-08-13 | Polyera Corporation | Attachable Device with Flexible Electronic Display Orientation Detection |
WO2015184045A2 (en) | 2014-05-28 | 2015-12-03 | Polyera Corporation | Device with flexible electronic components on multiple surfaces |
WO2016138356A1 (en) | 2015-02-26 | 2016-09-01 | Polyera Corporation | Attachable device having a flexible electronic component |
AU2019314508A1 (en) * | 2018-08-03 | 2021-01-14 | Q.E.D. Environmental Systems, Inc. | Self cleaning pneumatic fluid pump having poppet valve with propeller-like cleaning structure |
CN112392710B (zh) * | 2020-10-27 | 2022-06-17 | 杭州群科荟科技有限公司 | 一种汽车制动系统柱塞泵及其摩擦力检测方法 |
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DE112012002449B4 (de) | 2015-06-25 |
US9429154B2 (en) | 2016-08-30 |
CN103649537A (zh) | 2014-03-19 |
DE112012002449T5 (de) | 2014-03-13 |
US20140119964A1 (en) | 2014-05-01 |
JP5505386B2 (ja) | 2014-05-28 |
JP2013044294A (ja) | 2013-03-04 |
CN103649537B (zh) | 2016-03-16 |
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