WO2004067965A1

WO2004067965A1 - Valve structure and positive displacement pump using the valve structure

Info

Publication number: WO2004067965A1
Application number: PCT/JP2003/017013
Authority: WO
Inventors: Fumihiro Yaguchi
Original assignee: Shinano Kenshi Kabushiki Kaisha
Priority date: 2003-01-31
Filing date: 2003-12-26
Publication date: 2004-08-12
Also published as: AU2003292653A1

Abstract

A valve structure capable of increasing a pump efficiency by reducing a flow passage resistance and a positive displacement pump using the valve structure, the valve structure of a suction valve (41) opened when fluid is sucked into a pump chamber (26) and closed when the fluid is discharged from the pump chamber (26) or a delivery valve (42) closed when the fluid is sucked into the pump chamber (26) and opened when the fluid is discharged from the pump chamber (26), comprising valve elements (27) and (39) opening and closing flow passages (25) and (38), characterized in that the valve elements (27) and (39) are disposed aslant relative to the flow passages (25) and (38) in the contact state thereof with a valve seat (43).

Description

Valve structure and positive displacement pump using the same

The present invention relates to a valve structure used for a positive displacement pump and a positive displacement pump using the same.

Akira Background technology

Diaphragm pumps, which are one type of positive displacement pumps, are devices that change the volume of a diaphragm chamber (pump chamber) by reciprocatingly driving the diaphragm, thereby enabling the suction and discharge of air and other fluids. A general diaphragm pump mechanically reciprocates the diaphragm to change the volume of the diaphragm chamber.

FIG. 12 shows a conventional example (JP-A-2001-50165) in which an electromagnetic force is used as a driving force for driving a diaphragm. In the figure, 10a and 10b are pump chambers arranged opposite to each other, and each of the pump chambers 10a and 10b is partitioned into two diaphragm chambers by an elastic diaphragm 12. ing. Reference numeral 14 denotes a permanent magnet fixed to a central portion in the plane of each of the diaphragms 12, and 16 denotes an electromagnet arranged in the middle of the pump chambers 10a and 10b.

The electromagnet 16 changes the polarity of both ends of the magnet alternately between N pole and S pole by applying AC power to the coil, so that the electromagnet 16 and the permanent magnet 14 fixed to the diaphragm 12 are alternated. The magnetic force generated in the step causes the diaphragms 12 to repel or suck each other. Each diaphragm chamber partitioned by the diaphragm 12 is provided with an intake valve 18 and an exhaust valve 19, and when the diaphragm 12 is driven, air is sucked into the diaphragm chamber and exhausted. The required pump action is performed. The structure of the intake valve 18 shown in FIG. 13 can be considered.

Reference numeral 11 denotes a valve inserted in the flow path 13 and provided rotatably around a rotation shaft 11a at one end. 15 is a stopper, and 17 is a valve seat. The valve element 11 comes into contact with the valve seat 17, from the position perpendicular to the flow path 13 (solid line position), to the stopper 15, and is inclined at an angle of approximately 45 ° to the flow path 13 (The broken line position) around the rotation axis 11a.

When the air is sucked in the direction of the arrow, the valve body 11 rotates to the position indicated by the broken line and opens the flow path 13 due to the negative pressure, whereby the air is sucked into the diaphragm chamber. At this time, the exhaust valve 19 is closed.

When the air is exhausted from the diaphragm chamber, the valve body 13 rotates to the position indicated by the solid line by the positive pressure and contacts the valve seat 17 to block the flow path 13. At this time, the exhaust valve 19 is opened, air is exhausted, and a pump action is performed. The exhaust valve 19 has the same structure as the intake valve 18.

By the way, the valve structure of the positive displacement pump has the following problems.

That is, when air (fluid) is sucked (or exhausted or sent out), the valve body 11 is pushed open. However, since the valve body 11 is provided orthogonal to the flow path 13, particularly, In the initial state in which the valve element 11 opens the flow path 13, a large force is required to open the valve element 11, resulting in a large pressure loss and poor pump efficiency. There is also a problem that the response speed of the valve body 11 is slow.

Even when the valve body 11 contacts the stopper 15 to open the flow path 13, the valve body 11 forms an angle of about 45 ° with the flow path 13, and the flow path is There was a problem that the flow path resistance was high due to the large bending situation.

Therefore, the present invention has been made to solve these problems, and an object of the present invention is to provide a valve structure and a positive displacement pump capable of reducing flow path resistance and increasing pump efficiency. Disclosure of the invention

The present invention has the following configuration to achieve the above object.

That is, the valve structure according to the present invention is a valve used for a positive displacement pump, which opens when a fluid is sucked into a pump chamber and closes when a fluid is sent from the pump chamber, or a pump for suction. In the valve structure of the delivery valve which closes when the fluid is sucked into the chamber and opens when the fluid is delivered from the pump chamber, A valve element for opening and closing the flow path is provided, and the valve element is disposed to be inclined with respect to the flow path at a contact position with a valve seat.

Further, the valve body is provided so as to be inclined at least 30 ° with respect to the flow path.

Further, the valve body is formed as a valve body that opens and closes the flow path by rotating about a rotation shaft provided at one end side, and the valve body is in contact with a valve seat. The other end, which is opposite to the one end provided with the rotation shaft, is inclined with respect to the one end so as to be located on the rear side in the fluid flow direction. .

It is also preferable to provide a stopper for restricting further rotation of the valve body when the valve body rotates by a required angle in the direction of fluid flow.

In this case, it is preferable that the stopper is set so as to regulate the rotation at a position where the valve body is opened by 45 ° or more behind the position perpendicular to the flow path in the flow direction of the fluid. It is.

Further, it is preferable that the stopper is provided so as to be located within the projection area of the valve element viewed from the flow path direction when the valve element is opened to the maximum, so that the flow path resistance can be reduced.

In addition, the rotating shaft swings in a direction intersecting the axis of the rotating shaft between the rotating shaft and the bearing of the valve body so that the valve body can be in close contact with the valve seat. It is preferable to provide the required clearance as described above.

In this case, the rotation axis is 2 with respect to the axis of the bearing. It is preferable to set the clearance so that it can swing.

Further, the positive displacement pump according to the present invention opens when the fluid is sucked into the pump chamber, and closes when the fluid is sent out from the pump chamber, and sucks the fluid into the pump chamber. A positive displacement pump having a delivery valve which is sometimes closed and opened when a fluid is delivered from the pump chamber, wherein the suction valve or the delivery valve, or both the suction valve and the delivery valve are provided. In addition, any one of the above valve structures is used.

Further, in the diaphragm pump according to the present invention, the outer peripheral edge portion is fixed to the frame body, and the diaphragm is attached to the frame body so that the diaphragm and the A diaphragm chamber provided with the diaphragm body, a suction valve and a delivery valve provided in communication with the diaphragm chamber, and a driving unit for driving the diaphragm. The present invention is characterized in that any one of the valve structures described above is used for a delivery valve or both the suction valve and the delivery valve.

In this case, the driving means is provided on a permanent magnet attached to an outer surface of the diaphragm, and on an outer surface of the frame body facing the permanent magnet and opposite to the permanent magnet with the diaphragm interposed therebetween. And an electromagnetic force generating means. Alternatively, the driving means may include: an electromagnetic force generating means attached to an outer surface of the diaphragm; and the electromagnetic force generating means opposed to the electromagnetic force generating means and opposite to the electromagnetic force generating means with the diaphragm interposed therebetween. And a permanent magnet provided on the outer surface of the frame body.

Further, the means for generating the electromagnetic force may be constituted by an air-core energizing coil or an air-core energizing coil having an iron core. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a cross-sectional view (upper diaphragm position) showing the internal configuration of the diaphragm pump according to the present invention, and FIG. 2 is a cross-sectional view (lower diaphragm position) showing the internal configuration of the diaphragm pump according to the present invention. Yes, FIG. 3 is a top view of the diaphragm pump with the second frame body removed, FIG. 4 is a bottom view of the diaphragm pump, and FIG. 5 shows a configuration of an exhaust part of the diaphragm pump. FIG. 6 is a cross-sectional view, FIG. 6 is a block diagram showing an example of a drive circuit for driving the diaphragm pump of the embodiment, FIG. 7 is a block diagram showing another example of the drive circuit, and FIG. FIG. 9 is a block diagram showing still another example of the drive circuit. FIG. 9 is an explanatory diagram showing the structure of the suction valve. FIG. 10 is an explanatory diagram showing a state of the suction valve in FIG. 9 when the flow path is opened. And FIG. 11 is an explanatory view of the suction valve of FIG. 10 as viewed from the flow path side, FIG. 12 is an explanatory view of a conventional example of an electromagnetic diaphragm pump, and FIG. 13 is a conventional intake pump. It is explanatory drawing which shows an example of a valve. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. FIGS. 1 and 2 are cross-sectional views showing the configuration of an embodiment of an electromagnetic diaphragm pump which is an example of a positive displacement pump. FIG. 1 shows a state in which the diaphragm 20 is in an upper position (intake state). Indicates a state in which the diaphragm 20 is at the lower position (exhaust state). The displacement pump is not limited to the electromagnetic diaphragm pump, and the diaphragm may be mechanically reciprocated by connecting the diaphragm to an eccentric force that is eccentrically driven by a drive motor (see FIG. Not shown). In the following, an electromagnetic type will be described.

The electromagnetic diaphragm pump of the present embodiment has a storage space for movably storing the diaphragm 20 in a main body (frame body) 22 composed of a first frame body 22 a and a second frame body 22 b. And is assembled. That is, concave portions 23 a and 23 b for accommodating the diaphragm 20 are provided on the opposing surfaces of the first frame body 22 a and the second frame body 22 b, respectively. The main body 22 is movably supported in the thickness direction of the main body 22 in the space formed by the concave portions 23a and 23b.

20a is determined by a clamp provided with a predetermined width along the outer peripheral edge of the diaphragm 20.

FIG. 3 is a plan view showing a state where the diaphragm 20 is set in the first frame body 22a. As shown in the figure, the diaphragm 20 is a member formed in a circular shape, and the clamp portion (outer peripheral edge) 20 a is provided over the entire outer peripheral edge of the diaphragm 20. In other words, the diaphragm 20 is formed such that the entire periphery of the outer peripheral edge is formed along the opening edges of the concave portions 23 a and 23 b of the first frame body 22 a and the second frame body 22 b. The first frame body 22a and the second frame body 22b pinch and support each other. Reference numeral 24 denotes a fixing screw that presses and fixes the first frame body 22a and the second frame body 22b while the diaphragm 20 is pressed.

In FIG. 1, the diaphragm 20 and a first frame body 22 a arranged opposite to the diaphragm 20 constitute a diaphragm chamber 26, and the first frame body 22 a is a fixed wall, The diaphragm 20 corresponds to a movable wall. 2 5 is the first frame body 2 2 a An intake hole (flow path) 27 opened in the center is a valve body for controlling communication between the intake hole 25 and the diaphragm chamber 26. The suction valve (flow path) 25, the valve element 27, etc. constitute the suction valve 41. The valve body 27 opens the intake hole 25 when outside air flows into the diaphragm chamber 26 from the intake hole 25, and conversely, the intake hole 2 when air flows out of the diaphragm chamber 26 to the outside. It acts to block 5 and shut off the air flow. On the other hand, the second frame body 22b is provided with an opening 28 at the center, and air is allowed to flow through the opening 28 inside and outside the second frame body 22b. The diaphragm 20 reciprocates in the thickness direction of the main body (frame body) 22 with the outer peripheral edge portion clamped by the first frame body 22 a and the second frame body 22 b. And made of a material having a certain elasticity and durability such as rubber. Rubber such as EPDM is suitable for the material of the diaphragm 20, but the material is not particularly limited as long as it has the required flexibility and durability.

In the electromagnetic diaphragm pump of the present embodiment, a permanent magnet 30 is attached to the outer surface of the diaphragm 20 outside the diaphragm chamber 26. In the present embodiment, as shown in FIG. 3, the permanent magnet 30 formed in a rectangular flat plate shape is used, but a permanent magnet having an appropriate shape such as a circle can be used. The permanent magnet 30 is fixed to the center of the diaphragm 20. The permanent magnet 30 is magnetized in the thickness direction, and the polarity of the N-S pole may be either.

32 is a support plate fixedly provided on the outer surface of the diaphragm 20. The permanent magnet 30 is fixedly mounted in an opening provided at the center of the support plate 32. '

The support plate 32 has a ring-shaped portion (movable portion) 2 Ob having a predetermined width between the clamp portion (outer peripheral edge) 20 a of the diaphragm 20 (inside the outer peripheral edge) and the diaphragm. It is provided so as to cover 20 outer surfaces. The support plate 32 functions to support the diaphragm 20 such that the diaphragm 20 is driven in parallel with the thickness direction of the main body 22 while maintaining a flat surface. Thus, the diaphragm 20 is deformed and pushed only by the ring-shaped portion 20b sandwiched between the support plate 32 and the clamp portion 20a.

In this way, the entire diaphragm 20 is not deformed, and the diaphragm 20 By adopting a configuration in which only the ring-shaped portion 20b along the loop portion 20a is deformed, the durability of the diaphragm 20 is improved and the life can be extended. In the present embodiment, the ring shape 20b is formed to be thinner than other parts of the diaphragm 20 to improve the response of the diaphragm 20, and the diaphragm 20 is moved to the lower position. At this time, a flow space is formed with a slight gap between the inner surface (taper surface) of the concave portion 23a provided in the first frame body 22a.

The support plate 32 is provided with a through hole 32 a in a predetermined arrangement, and a stopper protrusion 20 c integrally formed with the diaphragm 20 is fitted into the through hole 32 a on the outer surface of the diaphragm 20. . The stopper projection 20c is provided to buffer the impact of the diaphragm 20 when the diaphragm 20 collides with the inner surface of the second frame body 22b, as shown in FIG. The support plate 32 is provided so that the end surface protrudes from the outer surface. In the present embodiment, the stopper projections 20c are provided at four locations that are equally spaced in the circumferential direction as shown in FIG. 3, but the number of the stopper projections 20c can be appropriately selected. .

In FIG. 1, reference numeral 34 denotes a back yoke provided on the back of the permanent magnet. The backpack 34 is provided so that a magnetic field acts efficiently on the permanent magnet, and is formed of a magnetic material such as iron. In the present embodiment, the back yoke 34 is formed in a flat plate shape having the same shape as the permanent magnet 30, and the back yoke 34 is attached so as to overlap the permanent magnet 30. In FIG. 1, reference numeral 40 denotes an energizing coil attached to the outer surface of the first frame body 22a. The current-carrying coil 40 drives the diaphragm 20 by applying a magnetic force to the permanent magnet 30. As shown in the figure, the energizing coil 40 is provided so as to wind around the intake valve 27 arranged at the center of the first frame body 22a. In this way, the current-carrying coil 40 is attached to the first frame body 22a in an arrangement facing the diaphragm 20. It is preferable that the thickness of the winding be as small as possible so that the energizing coil 40 can be stored in the first frame body 22a. FIG. 4 shows a state where the first frame body 22a is viewed from the lower surface side. An intake hole (flow path) 25 is opened at the center of the first frame body 22 a, and a conduction coil 40 is arranged around the suction valve 41.

In the present embodiment, generation of an electromagnetic force for applying an electromagnetic force to the permanent magnet 30 is performed. Although the air-core energizing coil 40 is used as the means, the electromagnetic force generating means is not necessarily limited to the air-core energizing coil 40. Even a current-carrying coil having an iron core can be arranged in the same manner as in the present embodiment by using an air-core iron core. In the present embodiment, the suction valve 41 is arranged at the center of the winding area of the energizing coil 40. However, the position where the suction valve 41 is arranged is not limited to the winding area of the energizing coil 40. The position of the first frame body 22a can be appropriately selected.

36 is a control board attached to the lower surface of the first frame body 22a. In the present embodiment, the control board 36 is attached to one half of the lower surface of the first frame body 22a except for the area where the energizing coil 40 is arranged. The control board 36 is provided with a drive circuit for controlling the time, polarity, and the like for energizing the energizing coil 40, whereby the electromagnetic diaphragm pump is appropriately mounted as a unit obtained by modularizing the electromagnetic diaphragm pump. It can be mounted on products. As shown in FIG. 1, the control board 36 is also housed within the thickness of the first frame body 22a, so that all necessary modules for driving the diaphragm pump are housed in the main body 22. An extremely compact electromagnetic diaphragm pump is constructed.

Note that, contrary to the above embodiment, the permanent magnet 30 may be attached to the outer surface of the first frame body 22a, and the energizing coil 40 may be attached to the outer surface of the diaphragm 20.

(Not shown). In this case, the energizing coil 40 moves together with the diaphragm 20, so that the control board and the energizing coil 40 are electrically connected by a flexible wire (not shown).

In FIG. 4, 38 denotes an exhaust pipe (flow path) extending from the first frame body 22a. Inside the first frame body 22a, a flow path 38a for communicating the exhaust pipe 38 and the diaphragm chamber 26 is provided.

FIG. 5 shows a flow path 38a provided inside the first frame body 22a. The end of the channel 38a opens in a tapered surface provided on the peripheral edge of the recess 23a formed in the first frame body 22a. As a result, the flow path 38a communicates with the diaphragm chamber 26, and the communication between the diaphragm chamber 26 and the flow path 38a also occurs when the diaphragm 20 moves to the lower position. Will be maintained.

A valve element 39 is attached in the middle of the exhaust pipe 38 and the flow path 38a. This valve The body 39 opens when air flows out of the diaphragm chamber 26 to the outside, and conversely blocks air flow when air flows into the diaphragm chamber 26 from the exhaust pipe 38. . The delivery valves 42 are composed of the flow paths 38, 38a, the valve body 39, and the like. 9 to 11 show an example of the valve mechanism of the suction valve 41 and the delivery valve 42 in more detail. Since both valves have the same configuration, the suction valve 41 will be described as an example.

Reference numeral 25 denotes the above-described intake hole (flow path), which communicates with the diaphragm chamber 26 on the downstream side. A valve seat 43 is formed in the intake hole 25. The valve seat surface of the valve seat 43 with which the valve element 27 abuts is provided to be inclined with respect to the intake hole (flow path) 25 as shown in the figure.

The valve element 27 rotates around a rotation shaft 27 a provided on one end side, contacts the valve seat 43, and opens and closes the intake hole (flow path) 25.

In the valve element 27, the movable part side (the side opposite to the rotating shaft 27 a) has a more inflow of air (fluid) than the rotating shaft 27 a side at the contact position with the valve seat 43. It is arranged at an angle so as to be located on the rear side in the direction.

The inclination angle of the valve element 27 is set to be 10 ° to 80 °, preferably 30 ° or more with respect to the flow path 25.

Reference numeral 4 denotes a stopper, which restricts further rotation of the valve element 27 when the valve element 27 rotates by a required angle in the direction of fluid flow during suction of air (fluid). It is preferable that the stopper 44 regulates the rotation at a position where the valve element 27 is opened by 45 ° or more behind the position orthogonal to the flow path 25 in the fluid flowing direction.

Further, as shown in FIG. 10, it is preferable that the stopper 44 be provided so as to be located in the projection area of the valve element 27 viewed from the flow path direction when the valve element 27 is opened to the maximum. You. As a result, an increase in the flow path resistance due to the stopper 44 can be prevented.

The rotating shaft 27 a of the valve element 27 is formed in a columnar shape as shown in the figure, and the rotating shaft 27 a is rotatable in a bearing hole 45 provided on the base side of the valve seat 43. It is inserted in. Then, the valve body 27 swings between the rotating shaft 27a and its bearing 45 in a direction in which the rotating shaft 27a intersects the axis of the rotating shaft 27a, and the valve body 27 The required clearance is provided so that 27 can be in close contact with the valve seat (surface) 43. In the present embodiment, the bearing holes 45 are rotated. The diameter of the moving shaft 27a is also made large so that the rotating shaft 27a can swing in the bearing hole 45. As a result, even when a twist is generated between the rotating shaft 27a and the valve body surface (the contact surface with the valve seat) in manufacturing the valve body 27, the valve body 27 can be surely secured to the valve seat ( (4) Since it comes into contact with 4 3, it is possible to prevent fluid leakage at the time of check, and to improve pump efficiency.

The above clearance is such that the rotation shaft 27 a is 2 with respect to the axis of the bearing hole 45. It is preferable to make the swingable as described above. The structure of the rotating shaft 27a and the bearing 45 is not limited to the above example. For example, the bearing side may be a pin, and the rotating shaft may be a shaft hole into which the pin enters.

In the above-described embodiment, the valve element 27 is configured to rotate about the rotation shaft 27a. However, the valve element 27 is moved in parallel with respect to the valve seat so that It may be configured to open and close (not shown). Even in this case, the valve body 27 is disposed so as to be inclined with respect to the flow path when the valve body 27 is in contact with the valve seat.

Subsequently, the operation of the electromagnetic diaphragm pump of the above embodiment will be described. FIG. 1 shows a state in which the diaphragm 20 is in the upper position and the air is sucked into the diaphragm chamber 26. That is, when a current in a direction that repels the permanent magnet 30 is applied to the energizing coil 40, the permanent magnet 30 repels due to the magnetic force, and the diaphragm 20 starts moving toward the second frame body 22b. I do. This operation is an intake operation. The valve element 39 closes the exhaust pipe (flow path) 38, the valve element 27 opens the intake hole (flow path) 25, and outside air flows into the diaphragm chamber 26. Get started. Then, by continuing the energization of the energizing coil 40, the diaphragm 20 moves until it comes into contact with the inner surface of the second frame body 22b, and outside air is introduced into the diaphragm chamber 26.

The operation of the valve body 27 to open the intake hole (flow path) is as follows. The valve body 27 is inclined with respect to the intake hole (flow path). From the initial stage of opening of the flow path by the body 27, the fluid (air) bends into the flow path obliquely (approximately 30 ° with respect to the flow path in the illustrated example) and enters the flow path. Not large, pressure loss is reduced, and pump efficiency can be increased accordingly. Also, the responsiveness of opening and closing the flow path is good. By the way, in the conventional type, in which the valve element closes the flow path perpendicular to the flow path, the fluid is bent almost at right angles to the flow path in the initial stage of opening the flow path by the valve element. Therefore, the flow path resistance becomes extremely large, and the pressure loss also increases accordingly. Also, the responsiveness of opening and closing the channel is not good.

The diaphragm 20 is stopped when the end face of the stopper projection 20c abuts on the inner face of the second frame body 22b. The operation of the diaphragm 20 is controlled by a drive circuit mounted on the control board 36. In consideration of the moving stroke amount of the diaphragm 20, the diaphragm 20 is actually operated at a high speed and the second frame 2 The electromagnetic diaphragm pump according to the present embodiment is controlled so that it does not collide with the inner surface of the second frame body 2b, so that the stopper projection 20c is brought into contact with the inner surface of the second frame body 22b. To prevent noise. Since the stopper projection 20c is formed integrally with the diaphragm 20 having flexibility such as rubber, noise when the stopper 20c contacts the second frame body 22b is reduced. In addition, it is also possible to attach another member having a high cushioning property to the stopper protrusion 20 c in order to reduce noise.

Next, when a current in the opposite direction is started to flow through the energizing coil 40, the permanent magnet 30 is attracted to the energizing coil 40 side, and the diaphragm 20 starts moving toward the first frame body 22a. I do. This operation is an exhaust operation. At this time, the intake hole 25 is shut off by the valve element 27, the valve element 39 opens the exhaust pipe (flow path) 38, and the air in the diaphragm chamber 26 is released. It begins to be discharged from the exhaust pipe 38.

At this time, the opening operation of the exhaust pipe 38 by the valve body 39 is also smoothly performed with good responsiveness because the valve body 39 is arranged inclined with respect to the flow path, and the pressure loss is also reduced. The pump efficiency can be increased.

FIG. 2 shows a state in which the diaphragm 20 has moved in a direction approaching the first frame body 22a, and the diaphragm 20 has finally contacted the inner surface of the first frame body 22a. is there. When the diaphragm 20 comes into contact with the first frame body 22a, the problem of noise is avoided because the diaphragm 20 itself comes into contact with the first frame body 22a. Since the diaphragm 20 is supported flat by the electromagnetic attraction of the energizing coil 40 and the support plate 32, the air introduced into the diaphragm chamber 26 efficiently passes through the flow path 38a. And is discharged from the exhaust pipe 38.

In particular, in the electromagnetic diaphragm pump of the present embodiment, since the permanent magnet 30 is arranged on the outer surface of the diaphragm 20, the diaphragm 20 is completely The first frame body 22 a can be moved to a position where it comes into contact with the inner surface thereof, whereby the air introduced into the diaphragm chamber 26 can be almost completely discharged.

When the air in the diaphragm chamber 26 is discharged, the greatest discharge force is required when the air remaining in the diaphragm chamber 26 is discharged last. In the case of a diaphragm pump, the point at which the diaphragm 20 contacts the inner surface of the first frame member 22 a is determined by the fact that the permanent magnet 30 attached to the diaphragm 20 and the energizing coil 40 are closest. This is the point where the magnetic force becomes the strongest, and the arrangement is the most efficient as the air discharge operation of the diaphragm chamber 26.

After the air is exhausted from the diaphragm chamber 26, the operation is switched to the intake operation by reversing the direction of current supply to the current supply coil 40 again. By controlling the energization of the energizing coil 40 in this way, it is possible to continuously perform the intake and exhaust operations by the diaphragm 20. In practice, the drive of the diaphragm 20 is controlled by appropriately controlling the current, frequency, and the like, which flow through the current-carrying coil.

Figures 6, 7, and 8 show examples of drive circuits for driving the electromagnetic diaphragm pump. The drive circuit 50 shown in FIG. 6 inputs a drive command signal and a current cutoff signal to the control circuit 52, and when the drive command signal is input, energizes the energizing coil 40 to drive the diaphragm 20. This is an example of a configuration in which In this case, the diaphragm 20 is configured to automatically return to one position of the intake or exhaust, and when the energizing coil 40 is energized, the electromagnetic force acts on the permanent magnet 30 to cause the other to return to the other position. It is controlled to move to the position. By attaching a return spring to the diaphragm 20 or the like, the diaphragm 20 can be automatically returned to the negative position.

The drive circuit 50 shown in FIG. 7 energizes the energizing coil 40 in the forward and reverse directions according to the drive command signal and the current cutoff command signal input to the control circuit 52, and This is an example in which a suction force and a repulsion force are alternately generated between the two to drive. It is possible to control the energizing coil 40 by applying an alternating current or a pulse current.

The drive circuit 50 shown in FIG. 8 uses a diaphragm position detecting element 54 to drive the diaphragm 20 by electromagnetic force by energizing the current-carrying coil 40. This is an example in which the movement position of the diaphragm 20 is detected and the drive of the diaphragm 20 is controlled. In FIG. 1, a reflective optical sensor 56a is provided on a first frame body 22a as a position detecting element 54 of the diaphragm 20, and an inner surface of the diaphragm 20 facing the reflective optical sensor 56a. An example in which a light reflecting coating 56b is provided on the rim is shown. In this case, in order to optically detect the moving position of the diaphragm 20, the first frame body 22a needs to be formed of a translucent material. FIG. 2 shows that a magnetic detection sensor 57 a is provided on the first frame body 22 a as a diaphragm position detection element 54, and is located on the outer surface of the diaphragm 20 so as to face the magnetic detection sensor 57 a. This is an example in which the detection magnet 57b is attached.

In the drive circuit 50 shown in FIG. 8, the position of the diaphragm 20 is constantly detected by the position detecting element 54, and the current and frequency of the current-carrying coil 40 are controlled based on the detection signal of the position detecting element 54. By doing so, the operation of the diaphragm 20 can be accurately controlled. For example, the impact force when the diaphragm 20 collides with the inner surface of the first frame body 22a or the second frame body 22b is reduced, the generation of noise is suppressed, and the diaphragm 20 has a long service life. Then, the control can be performed.

The current detection element 58 monitors the current flowing through the current-carrying coil 40 so that when the movement of the diaphragm 20 is deviated from the drive command signal, the current supplied from the drive circuit to the current-carrying coil 40 It is used to adjust the value and correct the deviation accurately. Responsiveness and high-accuracy control are possible because of current control. As described above, the electromagnetic diaphragm pump according to the present embodiment includes the diaphragm 20 in the main body (frame body) 22 including the first frame body 22a and the second frame body 22b. It is housed to form a diaphragm chamber 26, and the intake and exhaust operations are performed using electromagnetic force. As shown in Figs. 1 and 2, the structure of the main part of the diaphragm pump is extremely simple, and it is characterized in that it is thin and extremely compact. In addition, since the diaphragm 20 is designed to occupy a large movable area (volume) in the thin main body 22, the entire apparatus is formed in a compact form, so that power can be efficiently used. It has the characteristic that it is configured to perform the intake and exhaust functions. The first frame body 22a and the second frame body 22b constituting the main body 22 are not limited to non-magnetic metal as long as they have a predetermined strength, and may be formed of resin or the like. Of course it is possible. Since the electromagnetic diaphragm pump of the present embodiment has a configuration in which the energizing coil 40 is directly attached to the first frame body 22 a, the heat generated from the energizing coil 40 generates the first frame body 22. a and the second frame body 22 b are efficiently transmitted. Therefore, by forming the first frame body 22a and the second frame body 22b with a material having good heat conductivity, the air (fluid) introduced into the diaphragm chamber 26 is warmed and discharged. It becomes possible to do.

Since the electromagnetic diaphragm pump of the present embodiment can be formed in a very small size, it can be used for various purposes such as cooling of a notebook computer, a device for supplying air or fuel of a fuel cell, and medical equipment. A fuel cell has the advantage that the reaction of the cell can be promoted by supplying warm air. In addition, when used for medical equipment, it is possible to use the pump as an easy-to-use pump by heating and supplying the fluid.

Further, in the electromagnetic diaphragm pump of the present embodiment, the permanent magnet 30 is attached to the outer surface of the diaphragm 20 which is the outside of the diaphragm chamber 26, so that the permanent magnet 30 is provided inside the diaphragm chamber 26. There are no fasteners or adhesives for attaching the diaphragm, so that the air, fuel and blood sucked into the diaphragm chamber 26 can be supplied in a clean state without contaminating the air, fuel and blood. In particular, dust and gas generated from permanent magnets, fasteners, adhesives, and the like are likely to poison catalysts used in fuel cells and contain metal ions that cause deterioration of fuel cell functions. Therefore, an electromagnetic diaphragm pump in which the permanent magnet 30 is not provided in the diaphragm chamber 26 can be suitably used for a fuel cell.

In the above embodiment, the air intake / exhaust is described as an example. However, the diaphragm pump according to the present invention is not limited to gas such as air, but may be used for supply / discharge of fluid such as liquid. Can be. In the above-described embodiment, air is taken in from the front of the first frame body 22 a and exhausted from the side of the main body 22 (the side of the first frame body 22 a or the side of the diaphragm chamber 26). On the contrary, it is also possible to adopt a configuration in which air is taken in from the side surface of the main body 22 and exhausted from the first frame body 22a. You.

In order to make the frame body 22 thinner, a valve mechanism may be provided so as to suck and exhaust air from the side of the frame body 22. The invention's effect

As described above, according to the valve structure and the positive displacement pump according to the present invention, since the valve element is provided to be inclined with respect to the flow path, particularly in the initial stage of opening the flow path by the valve element, The fluid can be bent obliquely to the flow path and entered, and the flow resistance can be reduced, the pressure loss can be reduced, and the pump efficiency can be increased as compared to the case where the fluid enters at a right angle. it can. In addition, the responsiveness of opening and closing the flow path is excellent.

Also, in the case of a diaphragm pump, by providing the permanent magnet and the current-carrying coil on opposite sides of the diaphragm as described above, the diaphragm pump can be suitably reduced in size and thickness. It can be easily mounted on small devices and used. In addition, by installing a permanent magnet or an energizing coil on the outer surface of the diaphragm chamber, the diaphragm chamber is always kept in a clean space, and the air, fuel, and blood supplied from the diaphragm chamber are not polluted and the fuel is not contaminated. It can be suitably used for batteries, medical equipment, and the like.

Claims

The scope of the claims

1. A valve used in a positive displacement pump that opens when fluid is sucked into the pump chamber and closes when fluid is delivered from the pump chamber, or sucks fluid into the pump chamber. When the fluid is delivered from the pump chamber, it is closed when the fluid is delivered, and is opened when the fluid is delivered from the pump chamber.

Equipped with a valve to open and close the flow path,

A valve structure, characterized in that the valve body is disposed to be inclined with respect to the flow path at a contact position with a valve seat.

2. The valve structure according to claim 1, wherein the valve body is disposed so as to be inclined at least 30 ° with respect to the flow path.

3. The valve body is formed in a valve body that opens and closes the flow path by rotating around a rotation shaft provided on one end side,

When the valve body is in contact with the valve seat, the other end opposite to the one end provided with the rotation shaft is located rearward of the one end with respect to the fluid flow direction. 3. The valve structure according to claim 1, wherein the valve structure is arranged to be inclined.

4. The valve structure according to claim 3, wherein a stopper is provided for restricting further rotation of the valve body when the valve body rotates by a required angle in the direction of fluid flow.

5. The stopper according to claim 4, wherein the stopper restricts rotation at a position where the valve body is opened by 45 ° or more behind the position orthogonal to the flow path in the fluid inflow direction. Valve structure.

6. The valve according to claim 4, wherein the stop is provided so as to be located within a projection area of the valve element viewed from the flow path direction when the valve element is opened to a maximum. Construction.

7. The valve body is arranged so that the rotating shaft swings in a direction intersecting with the axis of the rotating shaft between the rotating shaft and its bearing so that the valve body can be in close contact with the valve seat. The valve structure according to any one of claims 3 to 6, wherein a required clearance is provided in the valve structure.

8. The rotating shaft is 2 with respect to the axis of the bearing. The valve structure according to claim 7, wherein the valve structure is swingable.

9. Suction valve that opens when fluid is sucked into the pump chamber and closes when fluid is sent from the pump chamber, and closes when fluid is sucked into the pump chamber, and fluid is sent from the pump chamber A positive displacement pump with an open delivery valve

9. A positive displacement pump comprising the valve structure according to any one of claims 1 to 8 used for the suction valve or the delivery valve, or for both the suction valve and the delivery valve.

10. A diaphragm chamber is provided between the diaphragm and the frame body by fixing the outer peripheral edge to the frame body, and a diaphragm is attached to the frame body, and communicates with the diaphragm chamber to send out a suction valve. And a valve for

The diaphragm pump provided with a driving unit for driving the diaphragm, wherein the suction valve or the delivery valve, or both the suction valve and the delivery valve, the valve according to any one of claims 1 to 8. A diaphragm pump characterized by using a structure.

1 1. The driving means comprises:

A permanent magnet mounted on the outer surface of the diaphragm;

10. The apparatus according to claim 10, further comprising: an electromagnetic force generating means provided on an outer surface of the frame body facing the permanent magnet and opposite to the permanent magnet across the diaphragm. Diaphragm pump.

1 2. The driving means,

Means for generating an electromagnetic force attached to the outer surface of the diaphragm;

A permanent magnet provided on an outer surface of the frame body facing the means for generating the electromagnetic force and opposite to the means for generating the electromagnetic force with the diaphragm interposed therebetween. Item 10. The diaphragm pump according to Item 10.

13. The diaphragm pump according to claim 11, wherein the electromagnetic force generating means is an air-core energizing coil or an air-core energizing coil having an iron core.