JPH1054363A - pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To decrease the number of part items so as to attain miniaturization of a device, by reducing a pump ripple at exhaust time while efficient pump operation can be made with a small change of torque when a pump is driven. SOLUTION: In an output shaft 5 of a motor 2, a crank pin 6 is eccentrically mounted. In a peripheral direction with the output shaft 5 serving as the center, an air bag 17 is equally arranged. In an operating pin 15 in an end part of an operating arm 13 turnably supported to the crank pin 6, a piston 18 integrally provided in the air bag 17 is bearing supported. By rotation with the output shaft 5 of the crank pin 6 serving as the center, the air bag 17 performs air suction/discharge successively by a fixed phase difference.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to a pump used for pressurizing a sphygmomanometer and the like.

[0002]

2. Description of the Related Art As a conventional pump used for a sphygmomanometer or the like, there is a pump as shown in FIGS.

Reference numeral 51 denotes a motor, 52 denotes an output shaft of the motor 51, 53 denotes a drive shaft eccentrically mounted on the output shaft 53, and 54 denotes a lid-shaped motor mounting base for mounting the motor 51. The motor mount 54 is provided at an appropriate position with a suction port 54a for introducing external air into the pump device.

[0004] Reference numeral 55 denotes a substantially rod-shaped operating rod, and 56 denotes a rectangular box-shaped case having an open surface. An elongated coupling hole 55 for coupling with the drive shaft 53 is provided at the center of the operating rod 55.
a, and mounting holes 55b for mounting the diaphragm body 57 are provided at both ends. The opening of the case 56 is fitted with the motor mount 54, and two insertion holes 56 a for inserting and holding the diaphragm 57 and the base 58 into the case 56 are provided on the bottom of the box.
A vent 56b for guiding the air introduced into the inside to the suction valve 57e is provided.

[0005] The diaphragm body 57 is an elastic body such as rubber and has a substantially rectangular shape. On the diaphragm 57, a diaphragm portion 5 having a slope and formed in a substantially rectangular oblique column shape is provided.
7a extends three-dimensionally with respect to the plane of the diaphragm body 57, and is three-dimensionally and integrally formed on the outer circumference of the output shaft 52 by 180 degrees.
Two bags are formed so that the slopes are located on the output axis side in opposition to each other, and a semicircular portion 57b serving as a bellows is provided over the entire circumference at the top of the diaphragm portion 57a. Further, a driving portion 57c for changing the volume in the diaphragm portion 57a to perform a pumping operation is provided at the center of the diaphragm portion 57a to increase rigidity in order to increase rigidity in order to increase rigidity from the bottom to the head of the diaphragm portion 57a. It is formed equally. A head 57d formed through a thin neck is provided at the tip of the driving unit 57c, and penetrates through the mounting hole 55b of the operating rod 55 to be mounted on the rod surface so that the driving unit 57c is mounted. Operating rod 5
5 is held. 57e is a diaphragm body 57
It is a tongue-shaped suction valve integrally formed on the upper side, and is provided 180 degrees opposite to the center axis direction of the diaphragm body 57.

Reference numeral 58 denotes a base having a rectangular plate shape, and an air chamber 59 is formed with a volume surrounded by the internal space of the diaphragm portion 57a and the base 58. The air chamber 59 includes a driving unit 57c.
The air chamber 59a on the outside in the radial direction of the motor and the air chamber 59b on the inside in the radial direction of the motor on the basis of. On the side where the base 58 presses the diaphragm body 57, the diaphragm portion 5
A substantially square standing wall 510 having a shape substantially similar to the three-dimensional surface 7a is provided. A mounting hole 58a for mounting an umbrella-shaped exhaust valve 511 made of an elastic material such as rubber is provided in the vertical wall 510, and a plurality of exhaust holes 58b are provided around the mounting hole 58a. A groove-shaped suction passage 58c for guiding the air passing through the suction valve 57e to the air chamber 59 is provided.

Reference numeral 512 denotes a lid having an exhaust port 512a at the center, which is integrally fixed to the motor mount 54, the case 56, the diaphragm 57 and the base 58 by screws 513.

[0008] Since the inner peripheral vertical surface of the diaphragm portion 57a is configured so that three of the four sides are in close contact with the upright walls 510b and 510c of the base 58, the diaphragm portion 57a moves when the driving portion 57c moves. Are prevented from moving inward and deforming. Since the same three sides of the outer peripheral surface of the diaphragm portion 57a as described above are configured to be in close contact with the inner peripheral surface of the insertion hole 56a of the case 56, the driving portion 5
When the 7c moves, the diaphragm surface is restricted from being displaced outward and expanded. For this reason, of the upright surface of the diaphragm portion 57a, the driving portion 57 having a slope is used.
Only the c-plane can vibrate, and the other plane is fixed between the case 56 and the base 58 without vibrating.

In the pump according to this conventional example, the rotational movement of the drive shaft 53 accompanying the rotation of the output shaft 52 of the motor 51 is controlled by the two diaphragm portions 57a opposed to each other by the elongated connecting hole 55a of the operating rod 55. Are converted into a reciprocating motion along a linear direction connecting the air chambers, and the pumping action is performed by alternately compressing and expanding the air chambers 59 disposed opposite to each other.

[0010]

However, in the pump according to the conventional example described above, since the long hole-shaped coupling hole 55a of the operating rod 55 is formed in a direction orthogonal to a line connecting the opposing driving parts 57c, Although the rotational motion of the drive shaft 53 is not transmitted in the direction orthogonal to the space between the opposing drive units 57c, no torque load is applied to the drive shaft 53.
A torque load is suddenly applied from the moment the diaphragm portion 57a moves in the compression / expansion direction, and the torque fluctuation during rotation of the motor is large, which appears as an impact sound when coming into contact with the elongated coupling hole.

Further, since the rotational motion of the output shaft 52 of the motor 51 is converted only into a reciprocating motion in a direction orthogonal to the elongated coupling hole, one or one opposing rod is opposed to one operating rod. Since only two air chambers can be formed, the capacity of each air chamber must be increased in order to secure a predetermined exhaust amount, and as a result, the pump ripple is increased.
On the other hand, if two or more air chambers are provided to reduce the pump ripple, the number of operating rods must be increased, which leads to an increase in the size of the device and an increase in the number of parts.

Further, among the rotational movements of the output shaft 52 of the motor 51, the movement in the direction orthogonal to the line connecting the opposing drive portions 57c is not used for the pumping operation, so that the energy conversion efficiency is poor. .

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems of the prior art, and it is an object of the present invention to reduce the torque fluctuation at the time of driving the pump and to achieve an efficient pumping operation. It is another object of the present invention to provide a pump that has a small pump ripple at the time of exhaustion and can reduce the number of parts to reduce the size of the device.

[0014]

In order to achieve the above object, a first aspect of the present invention has a variable volume hollow body for containing a fluid inside a wall surrounded by a wall, and the hollow bodies oppose each other. An eccentric rotary motion with respect to a drive shaft in a pump that changes the volume of the hollow body by changing the distance between two walls to suck the fluid into the hollow body and discharge the fluid from the hollow body. Has a movement transmitting means for changing the volume of the hollow body through, one of the two walls is a fixed wall whose movement with respect to the drive shaft is regulated, the other wall, An actuation wall operatively connected to the motion transmitting means, wherein a rotational motion of the drive shaft changes a position of the actuation wall with respect to the fixed wall while changing a distance between the actuation wall and the fixed wall. Especially To.

In this case, since it is not necessary to keep the posture of the working wall constant with respect to the fixed wall, various connecting mechanisms between the motion transmitting means and the hollow body can be realized. That is,
The degree of freedom in the arrangement of the hollow body is large, and the size of the pump can be reduced.

Here, the change in the space between the working wall and the fixed wall is not limited to the case where the space is changed in all portions of the two opposing walls, but also in the case where only a part of the space is changed and other portions are changed. The case where the distance does not change, for example, the case where the working wall rotates around a predetermined axis is also included.

The movement of the fixed wall with respect to the drive shaft is not limited to stationary, and it is sufficient that the movement of the working wall accompanying the rotation of the drive shaft restricts the distance between the working wall and the fixed wall from changing.

The posture of the working wall with respect to the fixed wall may be changed during the process of sucking and discharging the fluid.
The present invention is not limited to the case where it continuously changes throughout the ejection process.

The motion transmitting means includes a crank mechanism comprising a crank having a crankpin provided eccentrically with respect to a crankshaft as a drive shaft, and a connecting rod rotatably supported by the crankpin. There is a combination of an eccentric ring that is eccentric with respect to the shaft and an eccentric rod that slides with respect to this eccentric ring, and can change the volume of the hollow body by transmitting the eccentric rotational movement with respect to the drive shaft to the working wall. It is not limited to these if it exists.

If at least a part of the side wall connecting the fixed wall and the working wall of the hollow body is formed of a flexible member, the posture of the working wall with respect to the fixed wall is changed by the deformation of this member. The volume inside can be changed.

The operating mechanism in this case will be described below by taking a crank mechanism as an example, but the same applies to other motion transmitting means.

Here, if the deformation of the side wall is interlocked with the movement of the working wall without restricting the deformation of the side wall, the connecting portion of the connecting rod with the working wall is rotated by the rotation of the drive shaft in a plane perpendicular to the drive shaft. Performs a circular motion similar to a circular orbit. For example, when the working wall is restrained so as to swing about a predetermined axis and is also connected so as to swing with respect to the connecting rod, the connecting portion of the connecting rod with the working wall is formed on an arc. Reciprocating, but generally perform the orbiting motion as described above.

On the other hand, the movement of the working wall depends on the connection structure with the connecting rod which is operatively connected.

When the operating wall is connected so that the degree of freedom of movement of the connecting rod with respect to the connecting portion is zero, that is,
When the orbit is fixed to the connecting rod and makes a circular motion similar to the above-described circular orbit together with the connecting portion, the posture of the working wall changes with respect to the fixed wall whose movement with respect to the crankshaft is restricted, and the interval also changes. Therefore, the rotation of the crankshaft can be converted into a change in the volume of the hollow body.

When the operating wall is connected so that the degree of freedom of movement of the connecting rod with respect to the connecting portion is 1, for example, when the connecting wall is pivoted on a shaft provided at the connecting portion, the movement with respect to the crankshaft is also performed. Since the spacing changes while the posture of the working wall changes with respect to the restricted fixed wall, the rotation of the crankshaft can be converted into a change in the volume of the hollow body.

When the operating wall is connected so that the degree of freedom of movement of the connecting rod with respect to the connecting portion is 2, for example, when the operating wall is pivotally supported by a convex portion or a concave portion provided in the connecting portion, Since the interval changes while the attitude of the working wall changes with respect to the fixed wall whose movement with respect to the crankshaft is restricted, the rotation of the crankshaft can be converted into a change in the volume of the hollow body.

As described above, regardless of the connection structure of the working wall to the connecting rod, the orbital motion similar to the circular orbit of the connecting portion of the connecting rod to the working wall is converted into a change in the volume of the hollow body. The same applies to the case where another operating member is interposed between the connecting portion of the connecting rod and the operating wall.

Therefore, instead of converting only the predetermined radial movement of the circular motion of the crankpin due to the rotation of the crankshaft into a volume change of the hollow body, the entire circular motion is converted into a volume change of the hollow body. Therefore, torque fluctuation is small and energy conversion efficiency is improved. Further, there is no need for an operating rod having a long hole for converting the circular motion of the crankpin into a predetermined radial motion, so that there is no generation of an impact sound during operation.

Further, in the case where the operating wall has a connecting structure in which the degree of freedom of movement with respect to the connecting portion of the connecting rod is 1 or 2, a change in the posture of the operating wall following the deformation of the hollow body is allowed. The driving torque during operation can be reduced, and the energy conversion efficiency also improves.

At least a part of the side wall may be formed of an elastically deformable member such as a rubber-like elastic body. In this case, the side wall not only bends but also slightly expands due to pressure. However, if the elastic coefficient is set appropriately, the volume change due to the change in the space between the working wall and the fixed wall is not absorbed by the volume change due to the expansion of the side wall. You can do so.

The fixed wall and / or the operating wall may be formed of a flexible member or an elastically deformable member like the side wall, and the hollow body may be formed in a bag shape. By doing so, the number of parts can be reduced, and assemblability can be improved.

According to a second aspect of the present invention, in the first aspect, an operating member engaging with the operating wall by projecting a shaft parallel to the drive shaft at a connection portion of the motion transmitting means with the operating wall. Is provided on the shaft so as to be rotatable, and the operating member has a pressing portion for pressing the operating wall toward the fixed wall.

According to this configuration, the rotation of the operating member allows a change in the posture of the working wall of the hollow body, and also enables a drive following the change in the posture of the working wall due to the deviation of the fluid inside the hollow body. This eliminates the need for a force for operating against a change in the posture of the operating wall, thereby reducing drive torque and improving energy efficiency.

According to a third aspect, in the first or second aspect, the opposing surfaces of the operating wall and the fixed wall have shapes corresponding to each other.

Here, the term "corresponding shape" refers to a shape which can be brought into close contact when the space between the working wall and the fixed wall is lost. However, the present invention is not limited to the case where the entire surfaces of the working wall and the fixed wall have the shapes corresponding to each other, and only the portion where the working wall and the fixed wall can be in close contact with each other may have the corresponding shape.

In this way, even in the discharge process, even when the operation is performed until the gap between the working wall and the fixed wall is eliminated, no fluid remains between the working wall and the fixed wall, and high compression is achieved. Ratio is obtained and the volumetric efficiency is improved.

According to a fourth aspect, in the first to third aspects, a plurality of the hollow bodies are provided on a circumference centered on the drive shaft.

In this way, a certain amount of fluid can be sucked in
By performing the discharge by dividing the plurality of hollow bodies into a plurality of small volumes, the torque for operating each of the hollow bodies can be reduced, so that the torque fluctuation during the operation can be reduced.

Here, not only the case where all the hollow bodies are provided on the same circumference, the hollow bodies may be provided on a plurality of circumferences.

Further, if a plurality of hollow bodies having the same discharge amount are equally arranged in the circumferential direction, the symmetry of the force required for the operation with respect to the drive shaft becomes high, so that the torque fluctuation is small and the pump ripple is small.

However, it goes without saying that the discharge amounts of the respective hollow bodies may be different, and they may not be equally arranged in the circumferential direction.

According to a fifth aspect, in the fourth aspect, the plurality of hollow bodies suction and discharge the fluid at different phases.

With this arrangement, the discharge amount of each hollow body is subdivided and sequentially operated with a time lag.
Pump ripple is reduced.

According to a sixth aspect of the present invention, in the fifth aspect, the plurality of hollow bodies perform suction and discharge of the fluid while maintaining a certain phase difference with the hollow bodies adjacent in the circumferential direction. And

In this way, it is possible to prevent an increase in the pump ripple due to a change in the phase difference, and to reduce the pump ripple.

According to a seventh aspect, in the fourth to sixth aspects, the operating wall is disposed on an outer diameter side of the circumference, and the fixed wall is disposed on an inner diameter side of the circumference. I do.

In this way, when the operating wall is operated, the distance from the fulcrum to the power point becomes large, so that the driving torque is small and the torque fluctuation is small.

An eighth invention is characterized in that, in the fourth to sixth inventions, the operating wall is arranged on the inner diameter side of the circumference, and the fixed wall is arranged on the outer diameter side of the circumference. I do.

Since the motion transmitting means and the like can be arranged on the drive shaft side with respect to the hollow body, the size of the pump can be reduced.

A ninth invention is characterized in that in the fourth to eighth inventions, the plurality of hollow bodies are formed as an integral membrane member.

In this manner, the number of parts can be reduced,
The assemblability is improved.

As such a membrane member, a diaphragm made of a flexible member or an elastically deformable member can be used. Further, as such a member, there is a rubber-like elastic body or the like.

In a tenth aspect based on the ninth aspect, the membrane member has a suction valve that opens only when the fluid is sucked into each hollow body, and a suction valve that opens only when the fluid is discharged from each hollow body. A discharge valve for opening the valve is provided.

In this way, the number of parts can be reduced,
The assemblability is improved. In addition, by providing the suction valve and the discharge valve integrally with the membrane member, the size of the pump can be reduced.

[0055]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below based on the illustrated embodiment.

(First Embodiment) FIG. 1 shows a first embodiment of the present invention.
It is sectional drawing cut | disconnected by the surface which passes through the output shaft of the motor which shows the outline of the whole structure including the motor of the pump which concerns on 1st Embodiment.

FIG. 2 is an exploded perspective view showing a schematic structure of the pump body according to the first embodiment.

The pump 1 main body is provided on the output shaft side of the motor 2, and a discharge port 3 is provided on the opposite side of the pump 1 main body from the motor 2.

Reference numeral 5 denotes an output shaft of the motor 2 as a drive shaft;
Is a crank attached to the output shaft 5, and 6 is a crank pin eccentrically provided on the output shaft.

As shown in FIG. 3, a motor base 7 for attaching the pump 1 body to the motor 2 is fixed to an end face of the motor 2 on the output shaft side by screws (not shown).
The motor base 7 has a bottomed cylindrical shape. A circular hole 9 is formed at the center of the bottom surface 8 of the motor base 7, and is fitted to a bearing 10 of the output shaft 5. On the bottom surface 8, a screw hole 8 a for screwing the motor base 7 is provided symmetrically with the output shaft 4. Four screw holes 11 are equally arranged in the circumferential direction on the outer diameter side of the motor base 7, and an edge 11 a of the screw hole 11 protrudes toward the discharge port 3.

Reference numeral 12 denotes four arms 13 as connecting rods.
Is an operating arm integrally formed in a substantially cross shape. The crank pin 6 is inserted into a hole 14 formed in the center portion, and can rotate with respect to the crank pin 6. An operating pin 15 serving as a shaft body extending parallel to the output shaft is provided on the outer diameter end of each arm 13 as a connecting portion.
Are provided respectively.

Here, the crank 4 and the operating arm 12 constitute a motion transmitting means.

Reference numeral 16 denotes a diaphragm made of a rubber-like elastic material as a film member, and has a shape as shown in FIG. FIG. 4A is a perspective view of the diaphragm 16, and FIG. 4B is a side view of the same. Reference numeral 17 denotes an air bag whose one end is open, and a piston 18 as an operating member is integrally provided on the outer diameter side of the air bag 17. An insertion hole 19 for the operation pin 15 is provided at an end of the piston 18 on the motor 2 side. A flange 21 is provided at the end of the air bladder 17 on the opening 20 side, and the four air bladders are integrally joined at the flange portion. If the four air bladders are formed in a single diaphragm in this manner, the number of parts can be reduced and the pump 1 can be downsized.

FIG. 5A shows a part of the diaphragm viewed from the discharge port 3 side. 5B is a cross-sectional view taken along the line CC of FIG. 5A, and FIG. 5C is a cross-sectional view taken along the line DD of FIG. 5B.

On the outer diameter side of the opening 20 of the flange 21, a substantially semi-cylindrical projection 22 is provided. A thin intake valve 223 is provided on the outer peripheral side of the protruding portion 22 so as to be deformable with a substantially semi-cylindrical intake valve support portion 224 via a predetermined gap,
The circumferential end of the intake valve 223 is joined to the side end of the intake valve support 224, and the end of the flange 21 is joined to the side surface of the flange 21. An axial reinforcing rib 223a is provided at the center of the inner peripheral surface of the intake valve 223. A radial groove 2 is formed on the discharge port side end surface 225 of the intake valve support portion 224.
25a is engraved. The discharge port side end surface 225 of the intake valve support 224 slightly protrudes from the axial end surface of the intake valve 223.

On the inner diameter side of the opening 20 of the flange 21, a tongue-shaped deformable discharge valve 2 extending in the axial direction along the opening edge is provided.
3 are erected. An axial side reinforcing rib 23a is provided on the inner diameter side surface 231 of the discharge valve 23.

As described above, since the intake valve 223 and the discharge valve 23 are provided integrally with the diaphragm 16, the number of parts can be reduced and the size of the pump 1 can be reduced.

On the outer diameter side of the protrusion 22 of the flange 21,
A through hole 24 for conducting air is formed in the axial direction.

A sealing bead 25 surrounding the opening 20, the protruding portion 22, and the through hole 24 is provided on the end face 211 of the flange 21 on the side of the discharge port 3.

Reference numeral 26 denotes a substantially cylindrical cylindrical case having a bottom.

FIG. 6A is a view of the diaphragm case viewed from the motor 2 side, FIG. 6B is a sectional view taken along the line EE of FIG. 6C, and FIG. It is the figure seen from the side.

Four air bag storage portions 27 are equally arranged in the circumferential direction in the diaphragm case 26, and the discharge port 3 side end surface 261 is provided.
Is provided with a semicircular air bag insertion hole 28 for each air bag storage section. Four radial partitions 29 are provided radially inside the diaphragm case 26. The four partition walls 29 are joined at the center, and the air bag storage portions 27 are separated by the partition walls 29. Partition wall 29
An axial hollow portion 301 is provided in the central portion 30 of
It is open at the motor 2 side end surface.

A window 31 is provided at each end of the air bag accommodating portion 27 on the end face 262 of the diaphragm case 26 on the motor 2 side so as to engage the operating pin 15 with the diaphragm 16 via the diaphragm case 26. On the outer diameter side of the partition wall 29, a screw hole 32 penetrating in the axial direction is formed. Discharge port 3 side end surface 261 of diaphragm case 26
The step hole 321 protruding toward the discharge port 3 is formed around the screw hole 32 that opens to the side. On the outer diameter side of each air bag insertion hole 28 on the discharge port 3 side end surface 261 of the diaphragm case 26, an intake hole 33 for communicating the air bag storage portion 27 with the outside of the diaphragm case is formed.

A valve housing 34 is mounted on the discharge port 3 side of the diaphragm case 26.

FIG. 7A is a view of the valve housing 34 viewed from the motor 2 side, and FIG. 7B is a view taken along line FF of FIG. 7A.
FIG. 7C is a sectional view of FIG. 7A, and FIG.
(D) is a view of the valve housing 34 as viewed from the discharge port 3 side.

The valve housing 34 has a lid shape. On the motor 2 end face 341 of the valve housing 34, four recesses 35 each having a substantially semi-cylindrical cross section corresponding to the protruding portion 22 of the diaphragm 16 are equally arranged in the circumferential direction. ing. A groove 351 is provided on the outer diameter side of the concave portion 35 from the motor 2 side end surface 341 to the outer diameter side surface of the concave portion 35. Also, the recess 35
A tongue-shaped spacer 3 protruding toward the motor 2
Similarly, four are equally arranged in the circumferential direction.

The spacer 36 has a radially thick base 361 provided on the discharge port 3 side and a radially thin tip 362 provided on the motor 2 side of the base 361. The outer side surface 361a of the base portion 361 of the spacer 36 has a concave portion 3
5 is formed on the same surface as the inner diameter side surface 351 of the base 5, and the groove 37 at the center of the outer diameter side surface 361 a of the base 361 is formed in the concave portion 3.
5 from the bottom surface 352 to the end surface of the base 361 on the motor 2 side. The inner diameter side of the spacer 36 has an arc-shaped cross section, and the inner diameter side surface 363 is formed on the same plane as the side surface 381 of the concave portion 38. Inner diameter side surface 36 of spacer 36
The groove 39 provided in the center of the groove 3 extends from the motor 2 end of the spacer 36 to the vicinity of the discharge port 3 end of the side surface 381 of the recess 38. On the other hand, the groove 39 extends on the end face of the spacer 36 on the motor 2 side, and the end of the groove 39 reaches the outer diameter side surface 362a.

The motor 2 end face 3 of the valve housing 34
A recess 38 having a substantially star-shaped cross section is formed in the center portion surrounded by the four portions 41, and the discharge hole 41 is opened at the center portion of the recess 38 through a tapered portion 40 having a gradually decreasing diameter. I have. A screw hole 42 is formed in an outer diameter portion between adjacent recesses 35.
Are arranged equally in the circumferential direction, and the edge 42 of the screw hole 42 is
Reference numeral 1 protrudes toward the motor 2.

On the discharge port side of the valve housing 34, a discharge port 3 is protruded at the center, and a discharge hole 41 communicating with the motor 2 side is opened. On the outer diameter side, four screw holes 42 are equally arranged in the circumferential direction. The screw hole 42 is opened at the bottom of the concave portion 422 recessed from the discharge port side end surface 342, and a screw head for screwing the pump 1 body is accommodated in the concave portion 422.

The assembled state including the main body of the pump 1 and the main body of the motor 2 will be described with reference to FIGS. 1 and 2.

Each air bag 17 is press-fitted from the air bag insertion hole 28 in the end face 261 on the discharge port 3 side of the diaphragm case 26 and stored in the air bag storage section 27. The motor 2 side end surface 211 of the flange 21 of the diaphragm 16 contacts the discharge port 3 side end surface 261 of the diaphragm case 26. However, since the flange 21 of the diaphragm 16 is cut off at a portion corresponding to the step portion 321 of the discharge port 3 side end surface 261 of the diaphragm case 26, the step portion 321 is exposed.

The valve housing 34 is connected to the diaphragm 16
When the diaphragm 21 is mounted on the diaphragm case 26, the flange 21 of the diaphragm 16 is sandwiched between the discharge port 3 side end surface 261 of the diaphragm case 26 and the motor 2 side end surface 341 of the valve housing 34. At this time, the edge 421 of the screw hole 42 of the valve housing 34 fits into the screw hole 32 of the discharge port 3 side end face 261 of the diaphragm case 26, and the discharge port 3 side end face of the step portion 321 of the diaphragm case 26 is connected to the valve. Motor 2 side end surface 3 of housing 34
Contact 41. The height of the step 321 is the diaphragm 16
Since the thickness of the flange 21 is slightly smaller than the thickness of the flange 21, the flange 21 of the diaphragm 16 is sandwiched and fixed between the valve housing 34 and the diaphragm case 26.

The spacer 36 of the valve housing 34 is
The diaphragm 16 is inserted into the hollow interior through the opening 20 of each air bag 17, and the tip of the spacer 36 reaches near the motor 2 side end of the air bag 17. Tip 3 of spacer 36
Reference numeral 62 denotes a position substantially opposite to the inner diameter side of the piston 18 of the air bag 17.

The projection 22 of the diaphragm 16 is fitted into the recess 35 of the valve housing 34, and the discharge port side end face 225 of the projection 22 is in close contact with the bottom 352 of the recess 35. Further, the outer diameter side surface 2231 of the intake valve 223 is in close contact with the outer diameter side surface 353 of the recess 35 so as to be able to be separated from the outer diameter side surface 353, and opens and closes the intake hole 33 communicating with the groove 351 and the through hole 24. The inner diameter side end surface 2251 of the protruding portion 22 is in close contact with the inner diameter side surface 351 of the recess 35, but the inner diameter side surface 351 of the recess 35 and the outer diameter side surface 361 a of the spacer base 361.
The groove 225a of the discharge port side end surface 225 of the protrusion 22 and the hollow interior 17 of the air bag 17 are formed by the groove 37 provided at the center of the air bag 17.
And 2 are in communication.

The discharge valve 23 of the diaphragm 16 is provided with a concave portion 38 at the center of the motor 2 end face 341 of the valve housing 34.
Is stored in. Outer diameter side surface 232 of discharge valve 23 has concave portion 3
8 is closely contacted with the side surface 381 so as to be able to come and go.
Open and close.

The operating pin 15 is inserted into the insertion hole 19 of the piston 18.
And the operating arm 12 and the diaphragm 16 are engaged through the window 31 of the diaphragm case 26.

The operating arm 12 is mounted on the crankpin 6, and the edge 11 a of the screw hole 11 of the motor base 7 is screwed into the screw hole 32 of the motor 2 side end surface 262 of the diaphragm case 26.
Then, fixing screws (not shown) inserted through the screw holes 34 and 32 of the valve housing 34 and the diaphragm case 26 are screwed into the screw holes 11 to fix the pump 1 main body to the motor 2 main body.

The operation of the pump 1 according to this embodiment will be described.

The motor 2 is energized to rotate the output shaft 5. The crank 4 rotates with the rotation of the output shaft 5, and the crank pin 6 moves on a circumference around the output shaft 5.

[0090] As shown in FIG. 8, the crank pin 6 is eccentric by [delta] ₁ from the output shaft 5, the crank pin 6 moves the circle on a radius [delta] _1. Thereby, the arm 15
Operation pin 15 provided on the outer diameter side end portion of the maximum 2.delta. ₁ displaced in the radial direction.

The piston 18 supported by the operating pin 15
Performs the above displacement in conjunction with the movement of the operation arm 12.
Since the piston 18 is provided integrally with the air bladder 17, this displacement of the piston 18 causes a change in the volume of the air bladder 17.

Here, the flange 21 of the diaphragm 16
Is clamped and fixed between the diaphragm case 26 and the valve housing 34, so that the air bag 17 of the diaphragm 16 mainly operates with the movement of the operation arm 12. Further, since the piston 18 is provided integrally with the air bag 1, a joint portion with the air bag outer diameter portion 174 forms a pressing portion.

As described above, the air bladders 17 are equally arranged in the circumferential direction about the axis of the output shaft 5, and the piston 18 is provided integrally with the outer diameter portion 174 of the air bladder 17. Furthermore, since the inner diameter portion 173 of each air bag 17 is sandwiched between the spacer 36 and the center portion 30 of the diaphragm case 26, the radial movement of the inner diameter portion 173 is restricted.

Therefore, the outer diameter portion 174 of the air bladder 17 as an opposing operating wall is formed by the displacement of the operating pin 15 from the axis of the output shaft 5 accompanying the movement of the operating arm 12.
The radial distance from the spacer tip 362 as a fixed wall changes, and the volume inside the hollow body formed by the air bladder 17 and the spacer 36 changes.

In the process in which the piston 18 is displaced to the outer diameter side and the volume of the interior 172 of each air bag 17 increases (intake process), the pressure in the interior 172 of the air bag 17 becomes lower than the external pressure. 223 is deformed to the inner diameter side, is separated from the outer diameter side surface 353 of the concave portion 35 of the valve housing 34, and air flows into the air bladder 17 from the intake hole 33. At this time, the air flows in the order of the intake hole 33 → the through hole 24 → the groove 351 → the intake valve 223 → the groove 225a → the groove 37 → the air bladder 17. In this process, the outer diameter side surface 232 of the discharge valve 23 is in close contact with the side surface 381 of the recess 38 due to the pressure difference between the inside and outside of the air bag 17, and the discharge hole 41 is closed.

On the other hand, in the process in which the piston 18 is displaced to the inner diameter side and the volume of the inside 172 of each air bag 17 is reduced (exhaust process), the pressure inside the air bag 17 becomes higher than the outside pressure, so that the discharge is performed. The valve 23 is deformed to the inner diameter side and is separated from the side surface 381 of the concave portion 38 of the valve housing 34, and the air in the air bag 17 is discharged from the discharge hole 41. At this time, the air flows in the order of the air bag 17 → the groove 39 → the discharge valve 23 → the discharge hole 41. In this process, the outer diameter side surface 2231 of the intake valve 223 is in close contact with the outer diameter side surface 353 of the concave portion 35 due to the pressure difference between the inside and outside of the air bag, and the intake hole 33 is closed.

FIG. 9 is an AA sectional view showing a transition of the operation state of the pump 1 according to the present embodiment.

The crank pin 6 is rotated counterclockwise by 0 °, 90 ° with respect to the state where the crank pin 6 is positioned at the leftmost side with respect to the axis of the output shaft 5 toward the discharge port 3.
9, 180 and 270 degrees respectively.
(A), (b), (c), and (d) show.

As described above, in this embodiment, the piston 18, the intake valve 223, and the discharge valve 23 are provided for each air bag 17.
Are provided, so that the suction and exhaust processes are performed for each air bag. However, the pistons 18 of the air bladders 17 which are equally arranged in the circumferential direction around the output shaft 5 have substantially cross-shaped operating arms 12.
, Each air bag 17 performs an intake / exhaust operation with a substantially constant phase difference.

The air bag on the left side of FIG.
a and the piston are assumed to be 18a, and are distinguished in the following by adding the reference numerals b, c and d in the counterclockwise direction.

In FIG. 9A, the operating arm 12 is in a state of being displaced leftmost. Therefore, the piston 18a is farthest from the output shaft, and is in a state of shifting from the intake process to the exhaust process. On the other hand, the piston 18c is in the state closest to the output shaft 5, and the air bladder 17c is in the state of shifting from the exhaust process to the intake process, that is, in the state of being 180 ° delayed (advanced) from the air bladder 18a. . Also,
The piston 18b is in a state of going away from the output shaft 5, and is in an intake process in which the phase is delayed by 90 ° from the air bag 18a. Further, the piston 18d is in a state of approaching the output shaft 5, and is in an exhausting process in which the phase is advanced by 90 ° from the air bag 18a.

In FIG. 9B, the output shaft 5 is rotated by 90 °, and the operating arm 12 is displaced to the lowest position.
Accordingly, the piston 18a is approaching the output shaft 5, and the air bladder 17a is in the process of exhausting. At this time, the air bladders 17b, 17c, and 17d are in a state where the above-described constant phase difference is maintained with the air bladder 17a.

Hereinafter, in FIG. 9C, the output shaft is 180 °
The operating arm 12 has been rotated to the rightmost position. Therefore, the piston 18a is in the state closest to the output shaft 5, and the air bladder 17a is in the state of shifting from the exhaust process to the intake process. Also, in FIG. 9D, the output shaft 5 is
It has rotated 0 °, the operating arm 12 has been displaced to the uppermost position, the piston 18a has moved away from the output shaft 5, and the air bladder 17a is in the suction process. here,
As described above, the other air bladders operate while maintaining a constant phase difference with the air bladder 17a.

As described above, one rotation of the output shaft 5 corresponds to one cycle of intake and exhaust of each air bag 17, that is, one cycle of the pump 1 according to the present embodiment.

However, in this embodiment, the pump 1
Is composed of four air bladders 17 out of phase with each other by 90 °, so that the pump ripple is small as compared with a pump having a smaller number of cylinders having the same displacement per unit time.

Further, since the four arms 15 are formed as a single operating arm 12, the phase difference between the air bags operated by each arm is substantially constant, and the exhaust due to the variation in the phase difference between the air bags. Since the pump ripple does not increase at the time, the pump ripple at the time of pumping of the pump 1 can be reduced.

FIG. 9A, FIG. 9B, FIG.
As shown in (d), during one cycle in which the air bag 17 sucks and exhausts, the inner diameter side surface 1741 of the air bag outer diameter portion 174 and the distal end outer diameter side surface 3 of the spacer 36 oppose each other.
The angle formed with 62a has changed. The change in the angle will be described below.

As described above, the operating arm 12 is rotatably supported by the crank pin 6 at its center. On the other hand, an operating pin 15 provided at an outer diameter side end portion of the arm 13 causes the operating arm 12 to move the piston 18 on the outer diameter side.
The piston 18 is provided integrally with the elastically deformable air bladder 17. That is, on the outer diameter side of the operation arm 12, each operation pin 15 is in a state of being elastically supported by each air bag storage portion 27 of the diaphragm case 26. Accordingly, with the rotation of the crank pin 6, the center of the operation arm 12 rotates around the output shaft 5, and at the same time, each arm 13 swings with respect to the center of the operation arm 12.

At this time, the air bag 17 has the flange 21 fixed on the discharge port 3 side and the inner diameter portion 1 on the inner diameter side.
Since only 73 is fixed, the piston 18 and the operating pin 15 can move both radially and circumferentially. Therefore, the operating pin 15 and the piston 18
Performs a revolving motion in the air bag storage section 27 by drawing a locus similar to a circle.

Since the piston 18 is rotatably supported by the operating pin 15, when the air bag 17 is going to be deformed, the posture is changed integrally with the outer diameter portion 174 of the air bag 17. In addition, the air bag 17 can be deformed and can follow the deformation. For example, FIG.
In the case of the air bag 17a of FIG.
In the process of shifting to the state, the operating pin 15 is displaced downward along a locus similar to an arc and approaches the output shaft 5. At this time, the air in the air bladder 17a is gradually discharged.
The air 7a is deviated upward. With the deformation of the air bag 17a, the outer diameter portion 174a of the air bag 17a and the piston 18a are inclined upward. Similarly, in the other process, the outer diameter portion 174a of the air bag 17a and the piston 1
The posture of 8a changes.

Thus, the angle formed between the inner diameter side surface 1741 of the air bag outer diameter portion 174 and the outer diameter side surface 362a of the distal end portion of the spacer 36 changes.

As described above, in the present embodiment, the inner side surface 1741 of the air bag outer diameter portion 174 opposes the orbiting movement of the operating pin 15 and the piston 18 in the circular orbit.
By changing the distance while changing the angle between the outer diameter side surface 362a and the tip end outer diameter side surface 362a of the spacer 36, the air bladder 1 arranged in the circumferential direction around the output shaft 5
The suction and exhaust are performed by changing the volume of 7.

In other words, the outer diameter portion 174 of the air bag facing
By changing the distance between the inner diameter side surface 1741 and the outer diameter side surface 362a of the distal end portion of the spacer 36 while changing the angle between them, the volume of the air bag 17 is changed to perform suction and exhaust. Therefore, the movement of the operating arm 12 rotatably supported by the crank pin 6 can be converted into the intake / exhaust due to the volume change of the air bladder 17 arranged in the circumferential direction around the output shaft 5. is there.

As described above, in the pump 1 according to the present embodiment, suction and suction is performed by using only the radial displacement of the crankpin 6.
Since the intake and exhaust are performed using the entire circular motion of the crankpin 6 instead of performing the exhaust, the energy conversion efficiency is high.

Further, the inner side surface 1 of the air bag outer diameter portion 174
Since both the outer surface 741 and the outer diameter side surface 362a of the distal end portion of the spacer 36 are formed as flat surfaces, the air bag 17c shown in FIG.
The two surfaces are in close contact with each other, so that air not excluded between the two surfaces does not remain, a high compression ratio is obtained, and the volume efficiency is improved.

Further, the air bladder 17 arranged around the output shaft 5 sucks and absorbs the air using the entire circular motion of the crankpin.
Since air is exhausted, the number of air bladders 17 arranged in the circumferential direction can be set as appropriate. Therefore, if a large number of small air bladders 17 are arranged, the pump ripple at the time of exhaust can be reduced, and the torque required for operating one air bladder can be reduced, so that the torque fluctuation at the time of driving can be reduced. .

Also, as in the present embodiment, the piston 18
If the air bladder 17 is arranged on the outer diameter side, the distance between the crank pin 6 and the operating pin 15 increases, and when the air bladder 17 is operated, a part of the air bladder 17 is used as a fulcrum.
When the arm 13 is operated while rotating
When the lever 18 and the piston 18 form a lever, the force required for the operation is small, so that the driving torque is small and the torque fluctuation is small.

(Second Embodiment) FIG. 10 is a sectional view taken along a plane passing through an output shaft of a motor, schematically showing an entire structure including a motor of a pump 100 according to a second embodiment of the present invention. is there. FIG. 11 is an exploded perspective view of the pump 100 main body.

Since the motor, the motor base and the crankpin have the same configuration as in the first embodiment, the same reference numerals are given and the description is omitted.

The main body of the pump 100 is connected to the output shaft 5 of the motor 2.
The discharge port 101 is provided on the side of the pump 100 main body opposite to the motor 2.

At the tip of the crank pin 6, a columnar crusher 102 is detachably mounted. A hole 102 a that is rotatably engaged with the crank pin 6 is formed in an end surface of the crusher 102 on the motor 2 side. On the end face 1021 of the crusher 102 on the discharge port 101 side, four operating pins 103 as shafts parallel to the crankpin 6 are planted in the circumferential direction around the crankpin 6. Here, the crank 4 and the crusher 102 constitute a motion transmitting means.

At the tip of each operating pin 103, a piston 1
04 is mounted swingably. As shown in FIG. 12, the piston 104 has a substantially triangular prism shape in which the outer diameter side, which is a pressing portion, has a substantially circular arc shape. FIG. 12A shows the piston 104.
FIG. 12B is a view as seen from the discharge port 101 side, FIG. 12B is a view as seen from the outer diameter side, FIG.
FIG. 12D is a diagram viewed from the motor 2 side. A hole 1 for engaging with the operating pin 103 is provided in the support portion 105 on the inner diameter side.
05a is established, and the connecting portion 106 on the outer diameter side includes:
An engagement groove 107 that engages with a diaphragm described later is provided. The inner diameter portion of the piston 104 on the motor 2 side is:
The crusher is cut out in a shape corresponding to the shape of the side edge of the discharge port 101.

Reference numeral 108 denotes a diaphragm made of a rubber-like elastic material as a film member.

FIG. 13A is an axial center sectional view of the diaphragm 108, FIG. 13B is a sectional view taken along line KK of FIG. 13A, and FIG. .

The diaphragm 108 has an air bag 109 which is open on the discharge port 101 side of the pump 100. Four air bladders 109 are circumferentially arranged around the output shaft of the motor 2. A flange 111 is provided at an end of the air bag 109 on the opening 110 side, and the four air bags 109 are integrally joined at the flange 111 portion. Thus, the four bladders are combined into a single diaphragm 1
08, the number of parts can be reduced and the pump 100
Can be reduced in size.

A movable section 112 having a semi-cylindrical cross section is provided on the motor 2 side of the air bag 109.
A base 114 having a cylindrical cross section is provided on the side of the discharge port 101101 via a step 113. A thick reinforcing portion 115 is integrally formed on the outer diameter side of the movable portion 112, and the inner diameter side end surface 112a is a flat surface in a direction orthogonal to the radial direction. By making the outer diameter side of the movable portion 112 thicker, this portion is less likely to vibrate, and movement is regulated without providing another member such as the spacer 36 of the first embodiment, so that the number of parts is reduced. Can be achieved.

A columnar engaging portion 116 extends toward the motor 2 from a substantially central portion of the end face of the step portion 113 on the motor 2 side, and an outer diameter side of the engaging portion 116 is a plate-like joining portion extending in the axial direction. It is joined to the inner diameter side end surface 112 a of the movable portion 112 via 117. A guide portion 118 protrudes from the end face of the engagement portion 116 on the motor 2 side toward the motor 2. Here, the engaging part 116, the joint part 117, and the guide part 118 are formed integrally with the diaphragm 108 main body.

The end face 11 of the flange 111 on the discharge port 101 side
A tongue-shaped deformable intake valve 119 extending in the direction of the discharge port 101 is provided at an outer diameter side end of the opening 110 of the eleventh opening.
Two ribs 120 for reinforcement are provided on the inner peripheral surface of the intake valve 119 in the axial direction. The intake valve support 1192 is provided integrally on the inner peripheral surface of the base of the air bag 109, and the end of the support 1192 is connected to the discharge port 101 of the air bag reinforcement 115.
It has reached the side end face. The rib 120 is provided on the intake valve support 11.
92 are also provided on the inner peripheral surface.

The end face 11 of the flange 111 on the side of the discharge port 101
A tongue-shaped deformable discharge valve 121 extending in the direction of the discharge port 101 is provided integrally with the inner diameter side edge of the opening 110. The reinforcing rib 121 a is provided on the inner diameter side surface 1211 of the discharge valve 121. Two are provided in the axial direction. Rib 12
1a is an end face 1 on the discharge port 101 side of the flange central portion 122.
221 has been reached. The circumferential end of the discharge valve 121 formed along the edge of the opening 110 is joined to the circumferential end of the discharge valve of the adjacent air bag, and the four discharge valves form a substantially star shape.

As described above, since the intake valve 119 and the discharge valve 121 are provided integrally with the diaphragm 16, the number of parts can be reduced and the pump 100 can be downsized.

The end face 11 on the discharge port 101 side of the flange 111
A sealing bead 123 surrounding the opening 110 and the intake valve 119 is provided around the opening 110.

The diaphragm 108 is held by a substantially cylindrical cylindrical case 124 having a bottom.

FIG. 14A shows the diaphragm case 124.
FIG. 14B is a view of the motor 2 side, and FIG.
14C is a sectional view taken along line LL of FIG. 14, and FIG.
FIG. 14D is a sectional view as seen from the ejection port 101 side.

The diaphragm case 124 has an opening 125 on the side of the motor 2, and the bottom 126 on the side of the discharge port 101 is equally provided with four insertion holes 127 for inserting air bags in the circumferential direction. On the inner periphery of the side wall 128, four thick portions 129 extending in the axial direction and protruding toward the inner diameter side are equally arranged in the circumferential direction, and inside the thick portion 129 are fixed for fixing the motor 2 body. A screw hole 130 for inserting the screw is penetrated in the axial direction. The screw hole 130 is open on the outer diameter side between the adjacent insertion holes 127 at the bottom 126, and the periphery of the opening of the screw hole 130 protrudes toward the discharge port 101 to form a step 131. , Outlet 1 of bottom 126
The height of the step portion 131 from the 01-side end surface 1261 is set to be slightly smaller than the axial thickness of the flange 111 of the diaphragm 108. A flange 132 protruding toward the inner diameter side is provided on the inner peripheral surface of the end on the opening 125 side. The height of the flange 132 from the inner peripheral surface of the side wall 128 is the thick portion 1.
The height of the flange 132 is lower than the height of the flange 29 and the circumferential end of the flange 132 is joined to the side surface of the adjacent thick portion 129.

A valve housing 133 is mounted on the end of the diaphragm case 124 via the diaphragm 108.

FIG. 15A is a view of the valve housing 133 viewed from the motor 2 side, FIG. 15B is a sectional view taken along line NN of FIG. 15A, and FIG. 15C is a view of FIG. FIG. 15D is a cross-sectional view taken along the line P-P, and FIG.

The valve housing 133 has a lid shape.
On the motor 2 side end surface 1331 of the valve housing 133, four substantially cylindrical projections 134 are equally arranged in the circumferential direction. The inside of the protrusion 134 is hollow, and the inside of the hollow communicates with the outside through an opening 135 provided in the end surface 1332 on the discharge port 101 side. The motor 2 side end surface 1341 of the protrusion 134 is inclined toward the inner diameter side. An axially wide groove 1 is formed on the outer diameter side of the side surface 1342 of the protrusion 134.
36, and an axial groove 137 is also formed on the inner diameter side.

The end of the groove 136 on the discharge port 101 side is connected to a concave portion 138 provided in the axial direction on the outer diameter side of the protrusion 134, and the bottom surface 1361 of the groove 136 is in contact with the inner side surface 1381 of the concave portion 138. They form the same plane. An intake hole 139 that penetrates through the inside of the valve housing 133 body and communicates with the outside is opened on the outer diameter side surface 1382 of the concave portion 138.

At the center of the motor-side end surface 1331 of the valve housing 133, there is provided a concave portion 140 which is recessed from the outer diameter portion. At the center of the concave portion 140, a discharge hole 142 is formed via a taper portion 141 having a gradually smaller diameter. It is open. A screw hole 14 is formed in an outer diameter portion between adjacent protrusions 134.
4 are arranged equally in the circumferential direction, and the edge 1431 of the screw hole 143 on the motor 2 side protrudes toward the motor 2.

On the discharge port 101 side of the valve housing 133, a discharge port 101101 is provided at the center so as to protrude, and a discharge hole 142 communicating with the motor 2 side is opened. On the outer diameter side, four screw holes 143 are equally arranged in the circumferential direction.
The screw hole 143 opens at the bottom surface of the recess 1432 recessed from the end face 1332 on the side of the discharge port 101, and the screw head is housed in the recess 1432.

The assembled state including the pump 100 main body and the motor 2 main body will be described.

When the diaphragm 108 is inserted from the bottom 126 side of the diaphragm case 124, the motor 2 of the reinforcing portion 115 of the air bag 109 is attached to the end surface 1321 of the flange 132 on the inner peripheral surface of the diaphragm case 124 on the discharge port 101 side.
The side end surface 1151 comes into pressure contact with the diaphragm case side wall 12.
The outer peripheral surface 1152 of the reinforcing portion 115 of the air bag 109 contacts the inner peripheral surface 1281 of the air bag 8. Diaphragm case bottom 1
26, the end surface 1263a of the central portion 1263 on the side of the discharge port 101
The end surface 1222 on the motor 2 side of the central portion 122 of the flange of the diaphragm 108 is in contact with.

When the valve housing 133 is mounted via the diaphragm 108, the opening 11
The projection 134 is press-fitted from zero.

[0144] The projecting portion 134 is
4 and the base 114 is attached to the side surface 1342 of the protrusion 134.
Are in close contact with each other. The intake valve 119 is housed in a recess 138 of the valve housing 133,
19 has an outer diameter side surface 138 of the recess 138.
2 so as to be detachable and close to each other, and open and close the intake hole 139. The discharge valve 121 is housed in the concave portion 140 of the valve housing 133, and the outer diameter side surface 1212 of the discharge valve 121 is
The discharge hole 142 is opened and closed in close contact with the inner diameter side of the side surface 1342 of the fourth member so as to be able to be separated from and connected to the inner surface. Diaphragm 108 base 114
Is sandwiched between the projection 134 of the valve housing 133 and the diaphragm case 124.

The flange 111 of the diaphragm 108
Discharge port 101 side end face 1 of diaphragm case bottom 126
261 and the motor 2 side end surface 13 of the valve housing 133
31. Diaphragm case 124
Since the flange 111 of the diaphragm 108 is cut off at a portion corresponding to the step 131 of the screw hole 130 on the discharge port 1013 side, the step 131 is exposed. The edge 1431 of the screw hole 130 on the motor 2 side end surface 1331 of the valve housing 133 is
4 is fitted into the screw hole 130 on the end surface 1261 on the side of the discharge port 1013. The end surface of the step portion 131 of the screw hole 130 on the discharge port 1013 side of the diaphragm case 124 is in contact with the motor 2 side end surface 1331 of the valve housing 133. Discharge port 1013 side end surface 1261 of diaphragm case 124
The gap formed between the valve housing 133 and the motor 2 side end surface 1331 is set to be slightly smaller than the thickness of the flange 111 of the diaphragm 108, so that the diaphragm 108 is securely held.

The engagement groove 107 on the outer diameter side of the piston 104
Is composed of a large-diameter main engagement groove 1071 engaged with the engagement portion 116 of the diaphragm 108 and a guide groove 1072 engaged with the guide portion 118. The distal end of the guide portion 118 is connected to the motor-side end surface 12 of the diaphragm case 124 with the diaphragm 108 mounted in the diaphragm case 124.
It is formed so as to project from 62. Therefore, when the piston 104 is mounted from the guide portion 118 side, after the guide portion 118 is engaged with the entire engagement groove 107, the piston 104 is moved along the guide portion 118 and the engagement portion 116.
Is slid in the direction of the discharge port 101101, the engaging portion 116 is in the main engaging groove 1071, and the guide portion 118 is in the guide groove 107.
2 respectively. By doing so, the piston 104 can be easily mounted.

The main engagement groove 1071 of the piston 104
A protruding portion 1071a projecting into the groove is formed at an edge of the main engaging groove 1071, so that the main engaging groove 1071 and the engaging portion 116 are not easily separated by a movement in a direction perpendicular to the axis. This allows the movement of the piston 104 to
9 interlocks.

The edge of the hole 105a in the motor 2 side end surface 1051 of the support 105 facing the notch of the piston 104 is a step 1052 projecting toward the motor 2 side.
052 End face 1052a Discharge port 10 of crusher 102
It is in sliding contact with the first side end surface 1021. The end face 1041 of the piston 104 on the discharge port 101 side is in contact with the step 131 of the diaphragm 108. The rotation of the piston 104 pivotally supported by the operating pin 103 is performed by the connecting portion 106 facing the notch.
Of the inner surface 1061 of the crusher 102
2 is restricted by contact with the piston 10.
4 swings only within this range.

After the crusher 102 is mounted on the crankpin 6 and the edge 11a of the screw hole 11 of the motor base 7 is fitted into the motor 2 side opening of the screw hole 130 of the diaphragm case 124, the valve housing 133, the diaphragm A fixing screw (not shown) inserted through the screw holes 143 and 130 of the case 124 is screwed into the screw hole 11 of the motor base 7 to fix the pump 100 main body to the motor 2 main body.

The operation of the pump 100 according to this embodiment will be described.

The motor 2 is energized to rotate the output shaft 5. The crank 4 rotates with the rotation of the output shaft 5, and the crank pin 6 moves on a circumference around the output shaft 5.

As shown in FIG. 16, when the crank pin 6 is eccentric from the output shaft 5 by δ ₂ , the crank pin 6 moves on the circumference of the radius δ ₂ . As a result, the center of the crusher 102 rotatably supported by the crank pin 6 also moves on the same circumference as the crank pin 6, and the crusher 1
02 is provided with a maximum of 2δ _{2 in the} radial direction.
Displace.

The piston 10 supported by the operating pin 103
4 performs the above displacement while swinging in conjunction with the movement of the crusher 102. Since the piston 104 is engaged with the air bladder 109, the displacement of the piston 104 is
A volume change of 9 is produced. Here, the diaphragm 10
Since the flange 111 and base 114 of the diaphragm 8 are sandwiched and fixed between the diaphragm case 124 and the valve housing 133, the movable portion 112 of the diaphragm 108 mainly operates as the crusher 102 moves.
In addition, the reinforcing portion 115 of each air bag 109 is connected to the flange 132 of the diaphragm case 124 and the valve housing 133.
The outer diameter portion 1 of the movable portion 112 provided integrally with the reinforcing portion 115
121 is restricted in radial movement.

As described above, the air bladders 109 are equally arranged in the circumferential direction about the axis of the output shaft, and the piston 104 is engaged with the inner diameter portion 1122 of the movable portion 112 of the air bladder 109. Accordingly, due to the displacement of the operating pin 103 from the axis of the output shaft 5 due to the movement of the crusher 102, the outer diameter portion 1121 of the movable portion 112 as an operating wall and the inner diameter of the movable portion 112 as a fixed wall interlocked with the operating pin 103. Part 11
22 changes in the radial direction, and the volume inside the hollow body formed by the air bag 109 and the valve housing 133 changes.

In the process in which the piston 104 is displaced toward the inner diameter side and the volume of the interior 1091 of each air bag 109 increases (intake process), the pressure P in the interior 1091 of the air bag 109 becomes lower than the external pressure p. The valve 119 is deformed to the inner diameter side, is separated from the outer diameter side surface 1382 of the concave portion 138 of the valve housing 133, and air flows into the air bladder 109 from the intake hole 139. At this time, the air
9 → the intake valve 119 → the groove 136 → the air bag 109. In this process, the outer diameter side surface 1212 of the discharge valve 121
Is in close contact with the inner diameter of the side surface 1342 of the protrusion 134 due to the pressure difference between the inside and outside of the air bag 109, and the discharge hole 142 is closed.

On the contrary, the piston 104 is displaced to the outer diameter side,
In the process of reducing the volume of the interior 1091 of each air bag 109 (exhaust process), the pressure P in the interior 1091 of the air bag 109 becomes higher than the external pressure p. Projection 134 of
The air in the air bladder 109 is discharged from the discharge hole 142 at a distance from the inner diameter portion of the side surface 1342. At this time, the air flows into the air bag 109 → the groove 137 → the discharge valve 121 → the discharge hole 1
It flows in the order of 42. In this process, the outer peripheral surface 1192 of the intake valve 119 is in close contact with the outer diameter side surface 1382 of the recess 138 due to the pressure difference between the inside and outside of the air bag, and the intake valve 119 is closed.

FIG. 17 shows a pump 100 according to this embodiment.
FIG. 5 is a cross-sectional view taken along the line HH showing the transition of the operation state of FIG.

With the crankpin 6 facing the discharge port 101 and located at the leftmost position about the axis of the output shaft 5, the crankpin 6 is rotated counterclockwise by 0 °, 9 °.
FIG. 1 shows the state rotated by 0 °, 180 °, and 270 °, respectively.
7 (a), (b), (c) and (d).

As described above, in the present embodiment, since the piston 104, the intake valve 119 and the discharge valve 121 are provided for each air bag 109, the suction / exhaust process is performed for each air bag. However, the piston 104 of each air bag 109
Are connected by a substantially columnar crusher 102, so that each air bag 109 performs an intake / exhaust operation with a substantially constant phase difference.

The air bag on the left in FIG.
The reference numeral 9a and the piston are 104a, and the pistons are distinguished from each other by the reference numerals b, c and d in the counterclockwise direction.

In FIG. 17A, the crusher 102
Is in the state displaced to the left most. Therefore, the piston 10
4a is farthest from the output shaft, and is in a state of shifting from the exhaust process to the intake process. In contrast, the piston 10
4c is the state closest to the output shaft 5, and the air bag 10
Reference numeral 9c denotes a state in which the process shifts from the intake process to the exhaust process, that is, a state in which the phase is delayed (advanced) by 180 ° from the air bag 104a. Further, the piston 104b is in a state of moving away from the output shaft 5, and is in an exhausting process in which the phase is delayed by 90 ° from the air bag 104a. Further, the piston 10
4d is in a state of approaching the output shaft 5, and the air bag 10
The intake process is in a state where the phase is advanced by 90 ° from 4a.

In FIG. 17B, the output shaft 5 has been rotated by 90 °, and the crusher 102 has been displaced to the lowest position. Accordingly, the piston 104a is in a state of approaching the output shaft 5, and the air bag 109a is in a suction process. At this time, the air bladders 109b, 109c, and 109d are in a state of maintaining the above-described constant phase difference with the air bladder 109a, respectively.

Hereinafter, in FIG. 17C, the output shaft is 180
°, the crusher 102 is in a state of being displaced rightmost. Therefore, the piston 104a is in the state closest to the output shaft 5, and the air bag 109a is in the state of shifting from the intake process to the exhaust process. In FIG. 17D, the output shaft 5 has been rotated by 270 °, the crusher 102 has been displaced to the uppermost position, the piston 104a has been moved away from the output shaft 5, and the air bag 109a has been exhausted. It is in. Here, as described above, the other air bladder operates while maintaining a certain phase difference with the air bladder 109a.

As described above, one rotation of the output shaft 5 corresponds to one cycle of intake and exhaust of each air bag 109, that is, one cycle of the pump 1 according to the present embodiment.

However, in this embodiment, the pump 1
Is composed of four air bladders 109 out of phase with each other by 90 °, so that the pump ripple is small as compared with a pump having a smaller number of cylinders having the same displacement per unit time.

Further, since the four operating pins 103 are provided on the single crusher 102, the phase difference between the air bladders operated by the respective operating pins is substantially constant, and the phase difference between the air bladders is caused by the fluctuation of the phase difference between the respective air bladders. Since the pump ripple does not increase at the time of evacuation, the pump ripple at the time of evacuation of the pump 100 can be reduced.

FIGS. 17 (a), (b), (c),
As shown in (d), the air bag 109 performs suction and exhaust 1
During the cycle, the angle formed between the inner diameter side surface 11211 of the movable portion outer diameter portion 1121 and the outer diameter side surface 11221 of the movable portion inner diameter portion 1122 facing each other changes. The change in the angle will be described below.

As described above, the crusher 102 is rotatably supported by the crank pin 6 at its center. On the other hand, the end face 1021 of the crusher on the discharge port 101 side.
The crusher 102 is engaged with a piston 104 on the outer diameter side by an operating pin 15 provided in the, and the piston 104 is engaged with an elastically deformable air bag 109. That is, the crusher 102 is
Each operating pin 15 is in a state of being elastically supported by each air bag storage portion 27 of the diaphragm case 26. Accordingly, with the rotation of the crank pin 6, the center of the crusher 102 rotates around the output shaft 5, and at the same time, the crusher 102
The whole swings with respect to the center of the crusher 102.

At this time, the air bag 109 is
Side, the flange 111 is fixed, and the reinforcing portion 115 is only fixed on the outer diameter side.
04 and the operating pin 103 can move in both the radial direction and the circumferential direction. Accordingly, the operating pin 103 and the piston 104 make a circular motion in the diaphragm case 124 along a locus similar to a circle.

Since the piston 104 is rotatably supported by the operating pin 103, when the air bag 109 is about to be deformed, the posture is changed integrally with the inner diameter portion 1122 of the movable portion of the air bag 109. With the air bag 109
Can be allowed and can follow this deformation. For example, in the case of the air bag 109a of FIG. 17A, in the process of shifting from the state of FIG. 17A to the state of FIG. 17B, the operating pin 103 is displaced downward along a locus similar to an arc. Together with the output shaft 5. At this time,
Although the air is gradually sucked into the air bag 109a, the air sucked into the air bag 109a is biased upward as the operating pin 103 moves downward. This air bag 1
09a, the inner diameter of the movable portion 1 of the air bag 109a is increased.
22a and the piston 104a are inclined upward. Similarly, in other processes, the attitude of the movable portion inner diameter portion 1122a of the air bag 109a and the attitude of the piston 104a change due to the deformation of the air bag 109 accompanying the movement of the air in the air bag 109.

In this manner, the angle formed between the outer diameter side surface 11221 of the movable portion inner diameter portion 1122 of the air bag 109 and the inner diameter side surface 11211 of the movable portion outer diameter portion 1121 changes.

As described above, in the present embodiment, the inner diameter portion 1122 of the movable portion of the air bladder 109 facing the circular movement of the operating pin 103 and the piston 104 in a circle-like orbit.
By changing the distance between the outer diameter side surface 11221 of the movable portion and the inner diameter side surface 11211 of the movable portion outer diameter portion 1121 while changing the angle between them, the air arranged in the circumferential direction around the output shaft 5 The suction and exhaust are performed by changing the volume of the bag 109.

In other words, the distance is changed while changing the angle between the outer diameter side surface 11221 of the movable portion inner diameter portion 1122 and the inner diameter side surface 11211 of the movable portion outer diameter portion 1121 of the air bag 109 facing each other. Thus, suction and exhaust are performed by changing the volume of the air bag 109, so that the movement of the crusher 102 rotatably supported by the crank pin 6 is arranged in the circumferential direction around the output shaft 5. This can be converted into intake / exhaust due to a change in the volume of the air bag 109 thus performed.

As described above, the pump 10 according to the present embodiment is
In the case of 0, since the intake and exhaust are performed not by using only the radial displacement of the crankpin 6 but by using the entire circular motion of the crankpin 6, the energy conversion efficiency is high.

The movable portion outer diameter portion 112 of the air bag 109
1 and the inner diameter portion 1122 of the movable portion pressed by the outer diameter side surface 1061 of the connecting portion of the piston 104.
Since the outer diameter side surface 11221 and the outer diameter side surface 11221 both have a substantially arc-shaped cross section having substantially the same curvature, the air bag 109a shown in FIG.
The two surfaces are in close contact with each other, so that air not excluded between the two surfaces does not remain, a high compression ratio is obtained, and the volume efficiency is improved.

The air bladder 109 arranged around the output shaft 5 performs suction and exhaust using the entire circular movement of the crankpin 6, and is therefore arranged in the circumferential direction. Can be set as appropriate. Therefore, by arranging a large number of small air bags 109, the pump ripple at the time of exhaust can be reduced, and the torque required for operating one air bag can be reduced, so that the torque fluctuation at the time of driving can be reduced. .

Further, in the present embodiment, the movable portion inner diameter portion 1 which engages with the piston 104 is provided on the inner diameter side around the output shaft 5.
122, since the movable portion outer diameter portion 1122 is arranged on the outer diameter side, the piston 104 and the crusher 102 can be arranged on the output shaft 5 side with respect to the air bag 109, so that the pump 10
0 can be reduced in size.

[0178]

As described above, according to the first aspect, the distance between the working wall and the fixed wall is changed while the attitude of the working wall with respect to the fixed wall is changed. It is not necessary to keep the posture of the working wall constant, and various connection mechanisms between the motion transmitting means and the hollow body are made possible. That is, the degree of freedom in the arrangement of the hollow body is large, and the size of the pump can be reduced.

According to the second aspect of the present invention, a shaft parallel to the drive shaft is protruded from a connecting portion of the motion transmitting means with the working wall, and an operating member engaged with the working wall is rotated by the shaft. Since the operating member is provided with a pressing portion for pressing the operating wall toward the fixed wall side, the rotation of the operating member allows a change in the posture of the operating wall of the hollow body, and the inside of the hollow body. Driving that follows the change in the posture of the working wall due to the deviation of the fluid becomes possible, and a force for operating against the change in the posture of the working wall becomes unnecessary, so that the driving torque can be reduced and the energy efficiency can be improved.

According to the third aspect, the opposing surfaces of the working wall and the fixed wall have shapes corresponding to each other.
In the discharge process, no fluid remains between the working wall and the fixed wall, a high compression ratio is obtained, and the volume efficiency is improved.

According to the fourth aspect, since a plurality of hollow bodies are provided on the circumference around the drive shaft, a certain amount of fluid is sucked and discharged by a plurality of hollow bodies having a small volume. Thereby, the torque for operating each hollow body can also be reduced, so that the torque fluctuation during operation can be reduced.

According to the fifth aspect of the present invention, since the plurality of hollow bodies suck and discharge the fluid in different phases, the discharge amount of each hollow body is subdivided and the hollow bodies operate sequentially with a time lag. , Pump ripple is reduced.

According to the sixth aspect, since the plurality of hollow bodies each maintain a constant phase difference with the hollow body adjacent in the circumferential direction, an increase in pump ripple due to a change in the phase difference is prevented. Pump ripple can be reduced.

According to the seventh aspect, the operating wall is disposed on the outer diameter side of the circumference around the drive shaft, and the fixed wall is disposed on the inner diameter side of the circumference. Since the distance from the fulcrum to the power point becomes large, the driving torque is small and the torque fluctuation is small.

According to the eighth aspect, the working wall is arranged on the inner diameter side of the circumference around the drive shaft, and the fixed wall is arranged on the outer diameter side. Since the movement transmitting means and the like can be arranged, the size of the pump can be reduced.

According to the ninth aspect, since a plurality of hollow bodies are formed into an integral membrane member, the number of parts can be reduced, and assemblability is improved.

According to the tenth aspect, the membrane member has a suction valve that opens only when the fluid is sucked into each hollow body,
Since the discharge valve that opens only when the fluid is discharged from each hollow body is provided, the number of parts can be reduced, and the assemblability is improved. In addition, by providing the suction valve and the discharge valve integrally with the membrane member, the size of the pump can be reduced.

[Brief description of the drawings]

FIG. 1 is a partial cross-sectional view schematically illustrating an overall structure of a pump according to a first embodiment.

FIG. 2 is an exploded perspective view showing a schematic structure of a pump body according to the first embodiment.

FIG. 3 is a perspective view of a motor and a motor base of the pump according to the first embodiment.

FIG. 4A is a perspective view of a diaphragm of the pump according to the first embodiment, and FIG. 4B is a side view of the same.

5 (a) is a view of the lower side of the diaphragm of the pump according to the first embodiment viewed from the opening side, FIG. 5 (b) is a cross-sectional view taken along the line C-C, and FIG. It is DD half sectional view.

6 (a) is a view of a diaphragm case of the pump according to the first embodiment as viewed from the motor side, FIG. 6 (b) is a sectional view taken along the line EE, and FIG. 6 (c) is a diaphragm case thereof. FIG. 3 is a view as viewed from a discharge port side.

7A is a view of a valve housing of the pump according to the first embodiment as viewed from the motor side, FIG. 7B is a cross-sectional view of the same taken along line FF, and FIG. G sectional view, FIG.
(D) is the figure which looked at the same valve housing from the discharge port side.

FIG. 8 is a diagram illustrating a motion state of a crank and an operation arm of the pump according to the first embodiment.

FIG. 9 is an AA sectional view showing a transition of an operation state of the pump according to the first embodiment.

FIG. 10 is a partial cross-sectional view schematically showing an overall structure of a pump according to a second embodiment.

FIG. 11 is an exploded perspective view showing a schematic structure of a pump body according to a second embodiment.

12 (a) is a view of a piston of a pump according to a second embodiment as viewed from a discharge port side, FIG. 12 (b) is a view of the piston as viewed from an outer diameter side, and FIG. 12 (c) is FIG. 12D is a sectional view of the piston viewed from the motor side.

13A is an axial center sectional view of a diaphragm of a pump according to a second embodiment, FIG. 13B is a sectional view taken along the line KK, and FIG. 4C is an opening of the diaphragm. It is the figure seen from the part.

FIG. 14A is a view of a diaphragm case of a pump according to a second embodiment as viewed from a motor side, and FIG.
14B is a sectional view taken along line LL, FIG. 14C is a sectional view taken along line MM, and FIG. 14D is a view of the diaphragm case as viewed from a discharge port side.

FIG. 15A is a view of a valve housing of a pump according to a second embodiment as viewed from a motor side, and FIG.
15B is a sectional view taken along line NN, FIG. 15C is a sectional view taken along line PP, and FIG. 15D is a view of the valve housing as viewed from a discharge port side.

FIG. 16 is a diagram illustrating the motion state of the crank and the crusher of the pump according to the second embodiment.

FIG. 17 is an HH cross-sectional view showing a transition of an operation state of the pump according to the second embodiment.

FIG. 18 is a partial cross-sectional view schematically showing an entire structure including a motor of a pump according to a conventional example.

FIG. 19 is an exploded perspective view of the whole including a motor of a pump according to a conventional example.

[Explanation of symbols]

 Reference Signs List 1 pump 2 motor 4 crank 5 output shaft 6 crank pin 12 operating arm 13 arm 15 operating pin 16 diaphragm 17 air bag 173 air bag inner diameter portion 174 air bag outer diameter portion 18 piston 223 intake valve 23 discharge valve 100 pump 102 crusher 103 operation Pin 104 Piston 108 Diaphragm 109 Air bag 1121 Movable portion outer diameter portion 1122 Movable portion inner diameter portion 119 Intake valve 121 Discharge valve

Claims (10)

[Claims] 1. A hollow body having a variable volume for containing a fluid in an interior surrounded by a wall, wherein a volume of the hollow body is changed by changing a distance between two opposing walls of the hollow body. A pump for sucking the fluid into the hollow body and discharging the fluid from the hollow body, comprising a motion transmitting means for changing a volume of the hollow body through an eccentric rotational motion with respect to a drive shaft; One of the two walls is a fixed wall whose movement with respect to the drive shaft is regulated, and the other wall is an operation wall operatively connected to the movement transmitting means, A pump, wherein the distance between the working wall and the fixed wall is changed while the posture of the working wall with respect to the fixed wall is changed by the rotary motion. 2. A shaft parallel to the drive shaft is protruded from a connection portion of the motion transmitting means with the operation wall, and an operation member engaging with the operation wall is rotatably provided on the shaft. The pump according to claim 1, wherein the operating member has a pressing portion for pressing the operating wall toward the fixed wall. 3. The pump according to claim 1, wherein the opposing surfaces of the working wall and the fixed wall have shapes corresponding to each other. 4. The pump according to claim 1, wherein a plurality of said hollow bodies are provided on a circumference around said drive shaft. 5. The pump according to claim 4, wherein the plurality of hollow bodies suction and discharge the fluid at phases different from each other. 6. The pump according to claim 5, wherein the plurality of hollow bodies perform suction and discharge of the fluid while maintaining a certain phase difference with hollow bodies adjacent in the circumferential direction. 7. The operating wall is disposed on an outer diameter side of the circumference,
The pump according to any one of claims 4 to 6, wherein the fixed wall is arranged on the inner diameter side of the circumference. 8. The working wall is arranged on the inner diameter side of the circumference,
The pump according to any one of claims 4 to 6, wherein the fixed wall is arranged on an outer diameter side of the circumference. 9. The pump according to claim 4, wherein said plurality of hollow bodies are formed into an integral membrane member. 10. The membrane member is provided with a suction valve that opens only when fluid is sucked into each hollow body, and a discharge valve that opens only when fluid is discharged from each hollow body. The pump according to claim 9, wherein: