JP2005030341A - Diaphragm pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent operational failure of a motor, and to adopt various types of motors. <P>SOLUTION: When a crank table 10 is rotated, a driver 16 to which an oscillating part 14 is rotatably coupled is rocked, whereby diaphragm parts 28 are alternately reciprocated in the vertical direction to perform pump action. An output shaft 4 of the motor 2 is provided with a D-shape cut part 4a, and the crank table 10 is provided with a shaft hole 11 and a D-shape cut hole 11a where the output shaft 4 and the D-shape cut part 4a are fitted in the loose state. The thrust load applied to the crank table 10 by the pump action is received by a first rolling bearing 8 supporting the crank table 10 to freely rotate. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a diaphragm pump used for supplying a compressed fluid in a blood pressure monitor or the like.

In the conventional diaphragm pump, a crank base is fixed to the output shaft of a motor as a drive source, and the drive shaft is tilted and fixed at an eccentric position of the crank base, and a drive body that is rotatably supported by the drive shaft is driven. By reciprocating the child in the vertical direction, the diaphragm portion of the diaphragm also reciprocates, so that the pump chamber formed by the diaphragm portion contracts and expands, and the fluid sucked from the suction port is discharged from the discharge port ( For example, see Patent Document 1). In addition, the applicant could not find any prior art documents closely related to the present invention by the time of filing other than the prior art documents specified by the prior art document information described in the present specification. .
JP 2003-056465 A (paragraph “0018”, FIG. 1)

  In the above-described conventional diaphragm pump, a thrust receiver that locks the lower end of the output shaft is provided at the bottom of the motor case in order to receive the load in the thrust direction due to the pump action. However, since the conventional diaphragm pump described above has a structure for fixing the crank base to the output shaft of the motor, it is necessary to press the output shaft in the thrust receiving direction when the crank base is press-fitted into the output shaft. There is. Therefore, there is a problem that a predetermined gap provided between the commutator and the like attached to the output shaft and the bottom of the motor case, that is, play in the so-called thrust direction cannot be obtained, causing the motor to malfunction. It was. In addition, there is a problem that a motor having a structure not provided with a thrust receiver such as a coreless motor or a brushless motor cannot be employed.

  The present invention has been made in view of the above-described conventional problems, and a first object is to prevent malfunction of the motor. A second object is to make it possible to employ various types of motors.

To achieve this object, the invention according to claim 1 comprises a crank base that rotates as the output shaft of the motor rotates, a drive body that swings in conjunction with the rotation of the crank base, and the drive body. A diaphragm having a diaphragm portion that reciprocates by swinging of the diaphragm, and reciprocating the diaphragm portion causes a pump chamber formed by the diaphragm portion to contract and expand, and fluid sucked from the suction port is discharged from the discharge port. In a discharged diaphragm pump, a bearing that couples the crank base to the output shaft of the motor so as to restrict movement in the rotational direction and allow movement in the axial direction, and to receive an axial load on the crank base Is interposed between the crank table and the motor.
According to a second aspect of the present invention, in the first aspect of the invention, the crank base is provided with a swinging portion having an inclined rotation shaft, and the swinging portion is coupled to the drive body so as to be rotatable. Is.
The invention according to claim 3 is the invention according to claim 1, wherein a drive shaft is fixed to the crank table so as to be eccentric from the output shaft and inclined with respect to the output shaft. It is coupled to the drive body so as to be rotatable.
The invention according to claim 4 is the invention according to claim 3, wherein a non-contact portion that does not contact the bearing is provided in a portion of the crank table where the drive shaft is fixed.
The invention according to claim 5 is the invention according to claim 3, wherein a washer is interposed between the bearing and the crank base.
The invention according to claim 6 is the invention according to claim 3, wherein a support member is interposed between the bearing and the motor, and a groove for oil sump is formed at a portion where the bearing of the support member is in sliding contact. It is provided.

As described above, according to the present invention, since it is not necessary to press-fit the crank base to the output shaft of the motor, it is possible to prevent malfunction of the motor, and to install various types of motors. It becomes possible to adopt.
Further, according to the inventions according to claims 4 and 5, when a thrust load is applied to the drive shaft by the pumping action of the pump chamber, the load applied to the bearing is dispersed without being concentrated. Improves durability.
According to the invention of claim 6, since the coefficient of friction between the bearing and the support member becomes small, the wear of the bearing can be reduced, so that the durability of the bearing is improved.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view of a diaphragm pump according to a first embodiment of the present invention, FIG. 2 shows a crank stand, FIG. 1 (a) is a plan view, FIG. 1 (b) is a bottom view, and FIG. It is a bottom view of a drive body similarly. Note that “upper and lower” used to describe directions in the specification are directions for convenience of explanation, and are directions when the diaphragm pump according to the present invention is actually used. The lower direction does not necessarily match.

  The diaphragm pump generally indicated by reference numeral 1 in FIG. 1 includes a motor 2 as a drive source, and this motor 2 outputs power to a bottom portion 5 of a case 3 formed in a bottomed rectangular tube shape having an open top. The shaft 4 is attached by screws 7 so that the shaft 4 faces into the case 3 from a hole 6 formed in the bottom 5 of the case 3. On the upper side of the output shaft 4 of the motor 2, a D-cut portion 4a formed in a D-shaped cross section is provided. A raised portion 5a having a circular shape in plan view is integrally projected at the center of the bottom portion 5 of the case 3, and a recess 5b is provided at the center of the raised portion 5a. The above-described hole 6 is formed in the recess 5b. It is provided in the center. Reference numeral 8 denotes a first rolling bearing, and an outer ring is fixed to the edge of the recess 5b on the raised portion 5a of the case 3.

  Reference numeral 10 denotes a crank base formed in a substantially small cylindrical shape, and a shaft hole 11 is formed through the central portion thereof. A D-cut having a D-shaped cross section is formed above the shaft hole 11. A hole 11a is provided. The inner shapes of the shaft hole 11 and the D cut hole 11a are formed slightly larger than the outer shapes of the output shaft 4 and the D cut portion 4a. A small-diameter portion 12 is provided at the lower portion of the crank base 10, and a step portion 12 a is formed between the small-diameter portion 12 and the crank base 10. Further, a disc portion 13 inclined with respect to the shaft hole 11 is integrally provided on the upper portion of the crank base 10, and an annular placement portion 13 a is projected from the upper end of the disc portion 13. ing. On the mounting portion 13a, a swinging portion 14 formed in a small column shape so as to be inclined at the same angle as the disc portion 13 is integrally provided, and the diameter of the swinging portion 14 is described later. The rolling bearing 20 is formed to be slightly smaller than the inner diameter. That is, the rotation shaft 14 a of the swinging portion 14 is inclined by the angle α with respect to the output shaft 4 of the motor 2.

  The crankshaft 10 is inserted into the shaft hole 11 by inserting the output shaft 4 of the motor 2 and press-fitting the small diameter portion 12 into the inner peripheral surface of the first rolling bearing 8 so that the first rolling bearing 8 The case 3 is rotatably supported by the raised portion 5a. At this time, the stepped portion 12a of the crank base 10 is in contact with the upper end of the first rolling bearing 8, and a thrust load applied to the crank base 10 in the axially downward direction caused by the pump action described later is applied to this. It is received by the first rolling bearing 8. Further, the D cut hole 11a of the shaft hole 11 of the crank base 10 is fitted in the D cut portion 4a of the output shaft 4 of the motor 2 in a sliding state, and the crank base 10 is rotated along with the rotation of the output shaft 4. Rotates integrally. In other words, the crank base 10 is coupled to the output shaft 4 of the motor 2 so that movement in the rotational direction is restricted and movement in the axial direction is allowed.

  Reference numeral 16 denotes a drive body formed in a substantially umbrella shape. As shown in FIG. 3, a pair of drive elements 17 and 17 projecting outward at positions 180 ° out of phase with each other in the circumferential direction. Are integrally formed, and these driver elements 17 and 17 are formed so as to incline downward at the same angle toward the outside, and diaphragm attaching holes 17a and 17a are provided in the respective driver elements 17 and 17. . Further, an engaging projection 18 formed in an annular shape is integrally provided on the lower surface side of the driving body 16, and a spring retaining projection 19 is provided at the upper surface side central portion of the driving body 16. Are projecting together.

  Reference numeral 20 denotes a second rolling bearing, and the second rolling bearing 20 is attached to the driving body 16 by press-fitting and fixing the outer peripheral surface to the engaging convex portion 18 of the driving body 16. Further, the diameter of the inner peripheral surface of the second rolling bearing 20 is formed to be slightly larger than the diameter of the swinging portion 14 of the crank base 10 described above, and the second rolling element attached to the driving body 16 is formed. The inner peripheral surface of the bearing 20 is fitted to the swing portion 14 with a slight gap. That is, the swinging portion 14 is coupled to the drive body 16 via the second rolling bearing 20 so as to be rotatable.

  The diaphragm holder denoted by reference numeral 22 in the figure is formed in a box shape with an open bottom, and a spring-loaded convex portion 24 is integrally projected at the center of the lower surface of the ceiling portion 23, and the peripheral edge of the ceiling portion 23. The diaphragm is provided with two diaphragm part holding holes 25, 25, and the diaphragm holder 22 is fixed on the case 3.

  The diaphragm denoted by reference numeral 27 in the figure is made of a flexible material such as rubber, and is formed in a substantially rectangular shape by being connected to two diaphragm portions 28, 28 opened upward and the upper end portions of these diaphragm portions 28, 28. The formed flange 29 and two suction side valve bodies 30, 30 projecting from the flange 29 are integrally formed. A piston 31 having a substantially frustoconical cross section is formed integrally with the lower side of the diaphragm portion 28, and a projection 33 for locking is provided below the piston 31 via a narrow neck portion 32. It is integrally formed.

  The diaphragm 27 is press-fitted into the diaphragm mounting hole 17a of the driver 17 of the driving body 16 while elastically deforming the convex portion 33 of the diaphragm section 28, whereby the neck 32 is mounted in the diaphragm mounting hole 17a. Further, the diaphragm portion 28 is inserted into the diaphragm portion holding hole 25 of the diaphragm holder 22, so that the diaphragm holder 22 is mounted on the ceiling portion 23. Reference numeral 34 denotes a compression coil spring, which is elastically mounted between a spring-hanging convex portion 24 of the ceiling portion 23 of the diaphragm holder 22 and a spring-holding convex portion 19 of the driving body 16. 16 is urged downward.

  Reference numeral 35 denotes a discharge-side valve element, which is formed in a substantially flat plate shape by a flexible material such as rubber, and a raised portion 36 is integrally provided at the center of the surface side, and the back side of the raised portion 36 Is formed with an engagement recess 37 that fits into an engagement protrusion 41 of a valve holder 40 to be described later. Further, four ribs 38 project from the center side of the discharge side valve body 35 so as to extend radially.

  Reference numeral 40 denotes a valve holder formed in a flat, substantially rectangular parallelepiped shape. An engagement convex portion 41 for covering the discharge-side valve body 35 is integrally projected on the upper surface side of the center portion. Around the convex portion 41, an annular partition wall 42 is erected integrally. Further, two suction side valve holes 43, 43 that are closed by the suction side valve body 30 of the diaphragm 27 are provided outside the partition wall 42 of the valve holder 40. Two discharge side valve holes 44, 44 that are closed by the discharge side valve body 35 are provided.

  Accordingly, the suction side valve body 30 and the lower surface of the valve holder 40 constitute a check valve that restricts the flow of air from the pump chamber 55 described later to the suction space 52, and the discharge side valve body 35 and the valve holder 40 The upper surface constitutes a check valve that restricts the flow of air as a fluid from a valve chamber 53 (described later) to the pump chamber 55.

  Reference numeral 45 denotes a lid formed in a flat box shape with an opening at the bottom, and a cylindrical tube 46 is integrally provided at the center on the upper surface side. Forms a discharge port 47. On the back surface side of the lid body 45, a presser portion 48 formed in an annular shape in plan view so as to surround the cylindrical body 46 is integrally projected downward, and is flat so as to surround the presser portion 48. An engaging portion 49 formed in an annular shape is integrally projected downward. A suction port 50 is provided outside the engaging portion 49 of the lid body 45.

  In such a configuration, the diaphragm 27 is sandwiched between the valve holder 40 and the diaphragm holder 22 by placing the valve holder 40 to which the discharge side valve element 35 is attached on the diaphragm holder 22. Next, by assembling the lid 45 so as to be placed on the valve holder 40, the engaging portion 49 of the lid 45 comes into contact with the upper end of the partition wall 42 of the valve holder 40, and the holding portion 48 of the valve holder 40 discharges. It contacts the rib 38 of the side valve body 35.

  The contact portion between the valve holder 40 and the lid body 45 is welded, and the contact portion between the partition wall 42 and the engaging portion 49 is welded, thereby being surrounded by the lid body 45 and the partition wall 42 and the valve holder 40. A suction space 52 communicating with the suction port 50 and the suction side valve hole 43 is formed in the space. At the same time, a valve chamber 53 communicating with the discharge port 47 and the discharge side valve hole 44 is formed in a space surrounded by the lid body 45, the inside of the partition wall 42 and the valve holder 40.

  A pump chamber is provided between the diaphragm portion 28 of the diaphragm 27 and the valve holder 40 by attaching the lid 45 to the case 3 by a conventionally known method using a through bolt, a leaf spring, or a wire spring not shown. 55 is formed.

  By being configured in this way, when the motor 2 is driven and the output shaft 4 rotates, the D cut portion 4a of the output shaft 4 and the D cut hole 11a of the shaft hole 11 of the crank base 10 are engaged, The crank base 10 rotatably supported via the first rolling bearing 8 also rotates integrally, and the swinging portion 14 also rotates. Since the rotation shaft 14a is inclined by an angle α with respect to the output shaft 4 of the motor 2, the swinging portion 14 rotates in a state inclined by the angle α with respect to the output shaft 4 as the output shaft 4 rotates. A so-called swinging motion is performed. Since the swinging portion 14 is coupled to the drive body 16 via the second rolling bearing 20 so as to be rotatable, the drive body 16 swings with the swinging motion of the swinging portion 14. The two driving elements 17 and 17 are alternately reciprocated in the vertical direction. Accordingly, the two diaphragm portions 28 of the diaphragm 27 are alternately reciprocated in the vertical direction, so that the two pump chambers 55 are alternately contracted and expanded to perform a pumping action.

  That is, as shown in FIG. 1, when one of the two diaphragm portions 28 of the diaphragm 27 is lowered, the pump chamber 55 expands, so that the pump chamber 55 is in a negative pressure state. At this time, the discharge side valve body 35 functions as a check valve that restricts the flow of fluid from the valve chamber 53 through the discharge side valve hole 44 to the pump chamber 55. The valve hole 44 is closed. On the other hand, since the suction side valve body 30 opens the space between the suction side valve hole 43 and the pump chamber 55, the fluid that has flowed into the suction space 52 from the vent 50 of the lid body 45 is removed from the suction side valve hole 43. Into the pump chamber 55.

  When the output shaft 4 of the motor 2 further rotates and the diaphragm portion 28 of the expanded pump chamber 55 rises, the pump chamber 55 contracts, and the pressure of the fluid in the pump chamber 55 increases. At this time, the suction side valve body 30 functions as a check valve that prevents fluid from flowing from the pump chamber 55 through the suction side valve hole 43 to the suction space 52. Between 55 and the suction side valve hole 43 is closed. On the other hand, since the discharge side valve body 35 opens the discharge side valve hole 44, the fluid in the pump chamber 55 passes through the discharge side valve hole 44 and is discharged from the discharge port 47 through the valve chamber 53. Since the contraction / expansion operation of the pump chamber 55 is alternately and continuously performed in the two pump chambers 55, the fluid discharged from the two discharge side valve holes 44 to the valve chamber 53 is collected by the lid body 45. Are discharged continuously from one discharge port 47.

  Here, when the two diaphragm portions 28 and 28 move up and down by the pump chamber 55 being alternately contracted and expanded to perform the pumping action, the thrust chamber heading downward toward the crank table 10 via the driver 16 is provided. A load is added. At this time, the crank base 10 is allowed to move in the axial direction on the output shaft 4 of the motor 2, and the first rolling bearing 8 is interposed between the crank base 10 and the bottom 5 of the case 3, This thrust load is prevented from being applied to the output shaft 4 of the motor 2. Therefore, even if the motor 2 is not provided with a thrust receiver for the output shaft 4, it can be used for the diaphragm pump 1.

  In addition, since the shaft hole 11 of the crank base 10 is fitted in the sliding state in the output shaft 4 of the motor 2, there is no need to press-fit the crank base 10 into the output shaft 4. A predetermined amount of play in the thrust direction of the output shaft 4 due to the press-fitting work of the crank table 10 is not removed. For this reason, not only can the malfunction of the motor 2 be prevented, but it can also be applied to a motor having a structure not equipped with a thrust receiver, such as a coreless motor or a brushless motor.

  4 to 7 show a second embodiment of the present invention, FIG. 4 is a sectional view of a diaphragm pump, FIG. 5 is a plan view of a support plate, FIG. 6 is a plan view of a bearing, and FIG. It is a top view. In these drawings, the same or equivalent members described in the first embodiment shown in FIGS. 1 to 3 described above are denoted by the same reference numerals, and detailed description thereof is omitted as appropriate.

  4 is a support plate formed in a disk shape by a metal plate. As shown in FIG. 5, a center hole 111 is provided at the center, and around the center hole 111, Three oil sump grooves 112 extending radially from the center at equal angles to each other in the circumferential direction are provided, and two oil sump grooves 112 are disposed outside the sump grooves 112 at positions 180 ° out of phase with each other. Insertion holes 113 and 113 are provided. The support plate 110 is inserted into the insertion hole 113 and is fixed to the upper surface of the bottom portion 5 by a screw 7 that fixes the motor 2 to the lower surface of the bottom portion 5 of the case 3. The output shaft 114 of the motor 2 fixed to the case 3 faces the case 3 from the hole 115 of the bottom 5 of the case 3 and the center hole 111 of the support plate 110, and D having a D-shaped cross section on the upper side. A cut portion 114a is provided.

  Reference numeral 117 denotes a bearing formed in a circular shape by a thin plastic plate excellent in wear resistance and heat resistance, and has a central hole 118 at the center. Reference numeral 120 denotes a crank base formed in a small columnar shape, and a shaft hole 121 is provided at the center, and a D-cut hole 121a having a D-shaped cross section is formed on the upper side of the shaft hole 121. A press-fit hole 122 that is inclined with respect to the shaft hole 121 is recessed at a position eccentric with the shaft hole 121. The inner shapes of the shaft hole 121 and the D-cut hole 121a are formed slightly larger than the outer shapes of the output shaft 114 and the D-cut portion 114a of the motor 2, respectively. The bearing 117 is placed on the support plate 110 so as to be rotatable around the output shaft by inserting the center hole 118 into the output shaft 114 of the motor 2.

  The crank base 120 is configured such that the shaft hole 121 is fitted to the output shaft 114 of the motor 2 in a sliding state, and the D cut hole 121a is fitted to the D cut portion 114a of the output shaft 114 in a sliding state. The shaft 4 is coupled so that movement in the axial direction is allowed and movement in the rotational direction is restricted. Further, a bearing 117 is interposed between the crank base 120 and the support member 110, and the friction coefficient between the crank base 120 and the bearing 117 is larger than the friction coefficient between the bearing 117 and the support member 110. It is formed as follows. Reference numeral 123 denotes a drive shaft whose lower side is press-fitted into the press-fitting hole 122 of the crank table 120 so that the drive shaft 123 is inclined with respect to the output shaft 114 at a position eccentric from the output shaft 114. 120 is attached.

  A driving body 125 is formed by a boss 127 provided with a shaft hole 126 and a main body 128 formed integrally with the upper end of the boss 127, and the driving shaft 123 rotates in the shaft hole 126. It is inserted freely. The main body 128 is integrally formed with two driver elements 129 and 129 extending in opposite directions from the center in plan view, and these driver elements 129 and 129 are both at the same angle downward from the center toward the tip. The mounting hole 130 for attaching the diaphragm part 28 of the diaphragm 27 is provided in the front end side.

  In the diaphragm pump 101 of the second embodiment configured as described above, when the motor 2 is driven and the output shaft 114 rotates, the D cut portion 114a of the output shaft 114 and the D of the shaft hole 121 of the crank base 120 are rotated. Due to the engagement with the cut hole 121a, the crank base 120 also rotates integrally. At this time, since the friction coefficient between the crank base 120 and the bearing 117 is formed to be larger than the friction coefficient between the bearing 117 and the support member 110, the bearing 117 is integrated with the crank base 120. The bearing 117 slides on the support member 110. Here, since lubricating oil is supplied between the bearing 117 and the supporting member 110 by supplying lubricating oil to the oil reservoir groove 112 of the supporting member 110, the lubricating oil slides on the supporting member 110. Since the wear of the bearing 117 can be reduced, the durability of the bearing 117 is improved.

  As the crank base 120 rotates, the drive shaft 123 fixed to the crank base 120 in a state of being inclined from the axis of the output shaft 114 is eccentrically rotated so as to change the inclination direction around the output shaft 114. To do. Accordingly, the drive body 125 supported rotatably on the drive shaft 123 swings, and the two driver elements 129 and 129 reciprocate up and down alternately. Therefore, as in the first embodiment described above. The two diaphragm portions 28, 28 of the diaphragm 27 are also reciprocated in the vertical direction alternately, and the pump chambers 55, 55 are alternately contracted and expanded to perform a pumping action.

  As the pump chamber 55 alternately contracts and expands to perform the pumping action, similarly to the above-described first embodiment, when the two diaphragm portions 28 and 28 move up and down, the driving body 125 and the driving shaft 123 are driven. A thrust direction load is applied to the crank table 120 via the. At this time, the crank base 120 is allowed to move in the axial direction with respect to the output shaft 114, and the bearing 117 is interposed between the crank base 120 and the support member 110. To the output shaft 114 is prevented. Therefore, even if the motor 2 is not provided with a thrust receiver for the output shaft 114, the diaphragm pump 101 can be used.

  Further, since the shaft hole 121 of the crank base 120 is fitted in the sliding state on the output shaft 114 of the motor 2, it is not necessary to press-fit the crank base 120 into the output shaft 114. A predetermined amount of play in the thrust direction of the output shaft 114 due to the press-fitting work of the crank table 120 is not removed. For this reason, not only can the malfunction of the motor 2 be prevented, but it can also be applied to a motor having a structure in which a thrust receiver is not provided, such as a coreless motor or a brushless motor.

  FIG. 8 shows a first modification of the second embodiment of the present invention. FIG. 8A is a cross-sectional view of the crank table, FIG. 8B is a bottom view of the crank table, and FIG. ) Is a cross-sectional view of the main part showing a state where a load in the thrust direction is applied to the crank table, and FIG. 4D is a plan view of the bearing for explaining the range of the load applied to the bearing from the crank table.

  In the first modification, a recess 135 as a non-contact portion that does not contact the bearing 117 is provided on the lower surface side of the crank base 120 so as to correspond to the bottom portion 122a of the press-fitting hole 122 to which the drive shaft 123 is fixed. The recess 135 is provided in the right half of the lower surface of the crank table 120 in the drawing as shown in FIG. The depth H of the recess 135 is caused by a pump action by the diaphragm pump 101, so that a downward load F is applied to the crank table 120 via the drive shaft 123, and the right half of the crank table 120 is As shown in FIG. 2C, the recess 135 is formed to a depth that does not contact the bearing 117 when elastically deforming downward.

  Therefore, when a load F in the thrust direction is applied, the right half of the crank base 120 is elastically deformed downward, and the crank base 120 is slightly tilted clockwise in the figure. Therefore, the crank base 120 and the bearing 117 are the same. For the sake of convenience, a hatched area 136 in FIG. This region 136 is a range extending in the vertical direction so as to include the center hole 118 of the bearing 117, and the bearing 117 receives a load from the crank table 120 through this region 136. This region 136 becomes wider as compared with the case of FIG. 9 in which the recess 135 is not provided in the crank table 120.

  That is, as shown in FIG. 9A, when a thrust load F is applied to the drive shaft 123 while the entire lower surface of the crank table 120 is in contact with the upper surface of the bearing 117, the crank table 120 is moved to the drive shaft 123. Since only the portion corresponding to is elastically deformed, the range of the load applied from the crank base 120 to the bearing 117 is a region 137 corresponding to the area substantially the same as the cross-sectional area of the drive shaft 123 as shown in FIG. . Therefore, since the above-described region 136 is larger than the area of this region 137, when the recess 135 is provided in the crank table 120, the load applied to the bearing 117 is dispersed, so that the wear of the bearing 117 is reduced. Therefore, the durability of the bearing 117 is improved.

  FIG. 10 is a second modification of the second embodiment of the present invention. FIG. 10 (a) is a cross-sectional view of the main part showing a state in which a thrust load is applied to the crank table. b) is a plan view of a bearing for explaining a range of a load applied from the crank base to the washer, and FIG. 5 (c) is a plan view of the bearing for explaining a range of a load applied from the washer to the bearing.

  This second modification is characterized in that a washer 140 formed to have the same outer diameter as that of the bearing 117 is interposed between the crank base 120 and the bearing 117. With this configuration, when a thrust load F is applied to the drive shaft 123, the range of the load applied from the crank base 120 to the washer 140 is the same as that of the first modification described above. For the sake of convenience, a region 141 extending in a strip shape in the vertical direction is hatched. Since the washer 140 has the same outer diameter as the bearing 117 and is formed of a material having high rigidity, the range of the load applied to the bearing 117 from the washer 140 is the same as that shown in FIG. To the whole. Therefore, since the load applied to the bearing 117 is distributed throughout the bearing 117, the wear of the bearing 117 is further reduced, so that the durability of the bearing 117 is improved. In the second modification, a ring-shaped member formed of a material having high rigidity may be used instead of the washer 140.

It is sectional drawing of the diaphragm pump which concerns on the 1st Embodiment of this invention. The crank base of the diaphragm pump which concerns on the 1st Embodiment of this invention is shown, The figure (a) is a top view, The figure (b) is a bottom view. It is a bottom view of the drive body of the diaphragm pump which concerns on the 1st Embodiment of this invention. It is sectional drawing of the diaphragm pump of the 2nd Embodiment of this invention. It is a top view of the support plate in the diaphragm pump of the 2nd Embodiment of this invention. It is a top view of the bearing in the diaphragm pump of the 2nd Embodiment of this invention. It is a top view of the crank base in the diaphragm pump of the 2nd Embodiment of this invention. It is the 1st modification in the 2nd embodiment of the present invention, the figure (a) is a sectional view of a crank base, the figure (b) is a bottom view of a crank base, and the figure (c) is a crank. Sectional drawing of the principal part which shows the state in which the load of the thrust direction was added to the stand, The figure (d) is a top view of the bearing for demonstrating the range of the load applied to a bearing from a crank stand. It is a figure for comparing with the 1st modification in the 2nd embodiment of the present invention, and the figure (a) is a sectional view of the important section showing the state where the load in the thrust direction was added to the crank base, FIG. 2B is a plan view of the bearing for explaining the range of loads applied from the crank base to the bearing. FIG. 9A is a second modification of the second embodiment of the present invention, in which FIG. 11A is a cross-sectional view of the main part showing a state in which a thrust load is applied to the crank table, and FIG. A plan view of the bearing for explaining the range of the load applied from the crank base to the washer, and FIG. 8C is a plan view of the bearing for explaining the range of the load applied from the washer to the bearing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Diaphragm pump, 2 ... Motor, 3 ... Case, 4 ... Output shaft, 4a ... D cut part, 5 ... Bottom part, 8 ... 1st rolling bearing, 10 ... Crank stand, 11 ... Shaft hole, 11a ... D cut Hole, 14 ... Swing part, 16 ... Driver, 17 ... Driver, 20 ... Second rolling bearing, 22 ... Diaphragm holder, 27 ... Diaphragm, 28 ... Diaphragm part, 30 ... Suction side valve element, 35 ... Discharge Side valve element, 40 ... valve holder, 43 ... suction side valve hole, 44 ... discharge side valve hole, 47 ... discharge port, 50 ... suction port, 101 ... diaphragm pump, 114 ... output shaft, 114a ... D cut part, 120 ... Crank stand, 123 ... Drive shaft, 125 ... Drive body, 135 ... Recess, 140 ... Washer.

Claims (6)

  A crank base that rotates with the rotation of the output shaft of the motor, a drive body that swings in conjunction with the rotation of the crank base, and a diaphragm that has a diaphragm portion that reciprocates by the swing of the drive body, In the diaphragm pump in which the pump chamber formed by the diaphragm portion contracts and expands by reciprocating the diaphragm portion, and the fluid sucked from the suction port is discharged from the discharge port, the crank base is connected to the output shaft of the motor. And a bearing that receives an axial load on the crank table and is interposed between the crank table and the motor, and is coupled so as to restrict movement in the rotational direction and allow movement in the axial direction. Diaphragm pump.   2. The diaphragm pump according to claim 1, wherein a swinging portion having an inclined rotation shaft is provided on the crank base, and the swinging portion is coupled to the driving body so as to be rotatable.   2. The diaphragm pump according to claim 1, wherein a drive shaft is fixed to the crank base so as to be eccentric from the output shaft and inclined with respect to the output shaft, and the drive shaft is rotatable with respect to the drive body. Diaphragm pump characterized by being combined.   4. The diaphragm pump according to claim 3, wherein a non-contact portion that does not contact the bearing is provided at a portion of the crank base where the drive shaft is fixed.   4. The diaphragm pump according to claim 3, wherein a washer is interposed between the bearing and the crank base. 4. The diaphragm pump according to claim 3, wherein a support member is interposed between the bearing and the motor, and a groove for oil sump is provided at a portion where the bearing of the support member is in sliding contact. .

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