JP4918932B2 - Automatic urination processing apparatus and vacuum pump used therefor - Google Patents

Description

  The present invention relates to an automatic urination processing apparatus using a vacuum pump for sucking urine from a urine receiver, and a vacuum pump used therefor.

  Patent Document 1 describes an example of a urination suction device for a person who cannot easily move to a urination place by himself. In the urine suction device described in this publication, a urine storage container is interposed between a urine receiver and a suction pump as a suction source. When the urine receiver is urinated, the urine is detected and sucked into the urine storage container from the suction line. At that time, the suction state of the suction pump is controlled by a signal from a pressure sensor that detects a change in the pressure of the urine storage container.

  Many vacuum pumps are used as the suction pump. Examples of such a vacuum pump are described in Patent Document 2 and Patent Document 3. In the compressor described in Patent Document 2, a sliding member that continues lubrication by a self-lubricating action is provided in the rotary compressor in order to improve sliding characteristics and, consequently, efficiency. On the other hand, in the rotary vane type compressor and the vacuum pump described in Patent Document 3, the compression chamber and the pump chamber of the seal liquid are hermetically partitioned, and the seal liquid discharged from the pump chamber is sent to the seal portion and the lubrication portion. is doing.

JP 2003-126242 A JP 2002-195180 A JP-A-8-296575

  In the conventional urine suction device described in Patent Document 1, it is described that the operating state of a suction pump as a suction source is changed according to the pressure of a urine storage container. However, this Patent Document 1 does not sufficiently consider the size reduction and noise reduction of the suction pump. In order to increase the portability of the urine suction device, when the entire device is downsized, the suction pump needs to be downsized. The most effective way to reduce the size of the pump is to increase the rotation speed of the pump. However, if the rotation speed of the pump is increased, the positive displacement pump generally used for small pumps has a gap between the moving part and the stationary part. The relative gap becomes larger and the efficiency decreases. Also, simply increasing the speed increases noise. Since the urine suction device must be used not only outdoors but also at the bedside at night, noise reduction is essential.

  On the other hand, in the compressors described in Patent Document 2 and Patent Document 3, the reliability of the seal portion and the lubrication portion is improved in order to prevent the efficiency from being reduced due to downsizing or the like. However, since these compressors have not been specified for use in portable medical devices such as urination treatment devices, the structure is complicated from the viewpoint of emphasizing performance even though they are being miniaturized. It has become. In addition, since it is not used in a device that is expected to be used at night, the generation of noise and the reduction of life in intermittent operation are not sufficiently considered.

  The present invention has been made in view of the above problems of the prior art, and an object thereof is to reduce the size of the vacuum pump and improve portability. Another object of the present invention is to improve the reliability of a portable vacuum pump. Still another object of the present invention is to make it possible to use a urination treatment apparatus equipped with a vacuum pump even at night or outdoors.

In order to achieve the above object, the present invention provides an automatic urine treatment apparatus using a vacuum pump for sucking urine from a urine receiver, wherein the vacuum pump is made of resin, and a drive shaft of the vacuum pump and a motor shaft of the drive motor And a shaft joint in which a round hole mating with the motor shaft is formed on one side and a square hole mating with the driving shaft is formed on the other side, and is made of resin and is eccentric to the driving shaft. An eccentric shaft having an outer cylindrical portion, in which the metal drive shaft is integrated by insert molding, is made of resin, has a plate-like blade portion on the outer periphery, and a lower portion has a cylindrical shape. The piston is attached to the outer periphery of the eccentric shaft, and is made of resin. The eccentric shaft and the piston are accommodated, and the tip of the blade portion is arranged to protrude into the space formed on the inner peripheral surface. a cylinder which is a part of a cylinder Is a form the resin, is retained in the projecting portion of the cylinder in which the inner surface shape corresponding to the outer shape, by sandwiching the intermediate portion of the blade portion from the left and right, to regulate the movement of said blade portion, said piston A sliding cylinder that prevents the rotation of the cylinder, a suction flow path and a discharge flow path that are open in a pump chamber formed between the inner peripheral surface of the cylinder and the piston, and when the motor shaft rotates, The eccentric shaft and the piston are eccentrically moved. At this time, the movement of the blade is restricted by the sliding cylinder, the rotation of the piston is prevented, and the volume of the pump chamber is changed.

  According to the present invention, since the vacuum pump drives the resin piston through the resin shaft coupling and the eccentric shaft, the reliability is improved with a simple configuration, the noise generation source is reduced, and the night and outdoors. Not only can it be used, but also an automatic urine treatment device suitable for intermittent operation, light weight, excellent in heat resistance and wear resistance, suitable for weak acid resistance and weak alkali resistance in chemical resistance, and a vacuum pump used therefor Obtainable.

1 is a side sectional view of one embodiment of a portable vacuum pump according to the present invention. AA sectional drawing of FIG. The disassembled perspective view of the rotor part of the vacuum pump shown in FIG. The disassembled perspective view of the shaft coupling part of the vacuum pump shown in FIG. The disassembled perspective view of the drive shaft part used for the vacuum pump shown in FIG. The side view of the shaft coupling part used for the vacuum pump shown in FIG. The disassembled perspective view of the other Example of the shaft coupling used for the vacuum pump shown in FIG. The side view of the edge part of the drive shaft used for the vacuum pump shown in FIG. The front view and side view of the discharge valve holder 19 used for the vacuum pump shown in FIG.

  Hereinafter, an embodiment of a portable vacuum pump according to the present invention will be described with reference to the drawings. The vacuum pump shown in the present embodiment is mainly used in a urination processing apparatus. 1 is a longitudinal sectional view of the vacuum pump, and FIG. 2 is a sectional view taken along the line AA of FIG. 3 is an exploded perspective view of a main part of the vacuum pump shown in FIG. 1 and its BB cross-sectional view, FIG. 4 is an exploded perspective view of a shaft end portion of the vacuum pump shown in FIG. FIG. 2 is an exploded perspective view around the axis of the vacuum pump shown in FIG. 1.

  In the portable vacuum pump 1, a vacuum pump body 1 a is connected to one side surface of the drive motor 2 via a shaft coupling 21. The motor 2 drives the vacuum pump main body 1 at a rotational speed of 4000 to 7000 rpm. The motor 2 has a diameter of about 30 mm and an axial length of about 35 mm. The motor 2 is driven by a dry battery or secondary battery of about 4-9V.

  An intermediate portion in the axial direction of the drive shaft 10 connected to the motor shaft 2a via the shaft coupling 21 is fitted into a hole formed eccentrically inside the cylindrical eccentric shaft 11, and the eccentric shaft 11 is fitted to the motor shaft 2a. Eccentric movement around. A needle bearing 12 is fitted on the outer peripheral side of the eccentric shaft 11. The left and right axial sides of the eccentric shaft 11 are rotatably supported by ball bearings 15a and 15b. A balance weight 13 is attached to the contact surface 10f of the eccentric shaft 11 on the side opposite to the motor, that is, the left end in FIG. 1, with the balance weight contact surface 10e as a reference. The balance weight 13 is held on the eccentric shaft 11 by a stopper 14.

  In order to prevent scattering of a lubricant (not shown) applied to the ball bearing 15a held by the cylindrical ball bearing holding portion 5a, a conical lubricant reservoir 5b was attached around the ball bearing holding portion 5a. Similarly, a conical lubricant reservoir 4f was also attached to the holding portion of the ball bearing 15b. When the needle bearing 12 is used between the piston 3 and the eccentric shaft 11, a needle bearing fixing portion 11 d that holds the needle bearing 12 by pressing the inner ring side of the needle bearing 12 in the axial direction is formed.

A portion of the drive shaft 10 on the balance weight 13 side is covered with a cover 6 fitted to the flange 5. On one side surface 4c of the cylinder 4, a mounting plate 4d for attaching the vacuum pump 1 to the urination processing apparatus is provided. Furthermore, the end portion of the cylinder 4 on the motor 2 side is formed in a cylindrical shape, accommodates the shaft coupling 21, and fits into a fitting portion formed in the electric motor 2. Thereby, the motor 2 can directly support the cylinder 4. The outer peripheral portion of the cylinder corresponding to the pump chamber 4a is formed in a double manner, and a motor base 20 that holds the outer periphery of the motor 2 is attached to the end of the double portion on the motor 2 side. Therefore, the cylinder 4 is held by the motor 2 also by the motor base 20.

  The ball bearing 15b is held by a casing-integrated cylinder 4 which is a snowman-shaped container with one side face, the left side face in FIG. On the other hand, the left ball bearing 15 a is held by a ball bearing holding portion 5 a formed on the flange 5. The flange 5 is a plate-like member that covers the open-side surface of the cylinder 4, and the dedicated sheet 17 is disposed between the cylinder 5 and the cylinder 4 is hermetically fitted. The dedicated sheet 17 is a PTFE sheet and absorbs molding errors and assembly errors of the cylinder 4 and the eccentric shaft 11 made of a resin material, and the piston 3 and the sliding cylinders 7a and 7b, which will be described in detail below.

  Since the cylinder 4 slides on the dedicated sheet 17, a material having high slidability is used for the dedicated sheet 17. The dedicated sheet 17 can be deformed when the cylinder 4 slides. On the outer diameter side of the needle bearing 12, a piston 3 having a ring and a blade 3a formed by extending one circumferential portion of the ring outward is attached. An eccentric shaft 11, a needle bearing 12, and a piston 3 are accommodated in the cylinder 4.

  Sliding cylinders 7a and 7b that form part of the cylinder are sandwiched from the left and right at the intermediate part of the blade 3a. The sliding cylinders 7a and 7b are held by protrusions of the cylinder 4 having an inner surface shape that matches the outer shape of the sliding cylinders 7a and 7b. The tip of the blade 3 a protrudes into an elliptical cylindrical space formed on the inner peripheral surface of the protrusion of the cylinder 4. The lower portion of the piston 3 has a cylindrical shape, and the outer peripheral surface 3b faces the inner peripheral surface 4a of the lower portion of the cylinder 4 formed in a cylindrical shape. A small gap is formed between the piston 3 and the cylinder 4 so that the sealing performance can be maintained even in the narrowest part. The piston 3 rotates in the cylinder 4. When the piston 3 pivots at a constant radius, the crescent-shaped space 4b formed between the inner peripheral surface 4a of the cylinder 4 and the piston 3 also moves following it. Then, the gas is sucked from the suction flow path 8 and discharged to the discharge flow path 9.

  In the vicinity of the holding portions of the sliding cylinders 7a and 7b of the cylinder 4, a suction channel 8 and a discharge channel 9 are formed in a direction perpendicular to the drive shaft 4 and in the horizontal direction. The suction flow path 8 and the discharge flow path 9 are open to the pump chamber 4b. A valve seat 9b is formed in the discharge flow path 9, and the discharge valve 9a is in contact with the valve seat 9b. The discharge valve 9a is a silicon sheet having a thickness of 0.5 mm. The discharge valve presser 19 is pressing the discharge valve 9a to the non-discharge side. The discharge valve 9a attached to the discharge flow path 9 is provided as close to the blade 3a as possible on the cylinder inner peripheral surface 4a in order to reduce the dead volume. In the present embodiment, a valve seat 9b is formed by forming a hole having a diameter larger than that of the discharge passage 9 on the cylinder side surface 4c on the discharge side.

  Details of the discharge valve retainer 19 are shown in FIG. FIG. 2A is a front view thereof, and FIG. 2B is a side view thereof. The discharge valve presser 19 is formed by processing a round bar. That is, the through hole 19y is processed at the center of the round bar, and the back side is stepped by the discharge valve jumping width 19d in the axial direction. A part of the step is notched obliquely in the height direction in FIG. A slot 19j which is a groove cut out in the diameter direction is formed on the front side of the round bar, and a round hole 19x having a diameter larger than that of the through hole 19y is formed up to an intermediate portion in the axial direction. A hexagonal hole 19i for attaching the discharge valve retainer 19 with a hexagon wrench is formed on the back side of the round hole 19x. The outer diameter 19a of the discharge valve retainer 19 is 5.0 mm.

  A discharge valve 9 a having substantially the same diameter as the discharge valve presser 19 is disposed on the back side of the discharge valve presser 19. The discharge valve 9 a is a PTFE disc sheet having a thickness of 0.1 mm, and only the upper end to the stepped portion is pressed by the discharge valve presser 19 in accordance with the shape of the discharge valve presser 19. Therefore, the lower part from the stepped part is bent to the left and right by the pressure of the discharge flow path 9. Here, the valve presser length 19b, which is the length from the upper end to the stepped portion, is 1.15 mm. The valve opening angle 19c, which is a notch angle of the stepped portion, is 45 degrees. The discharge valve 9a is bent with the valve opening fulcrum portions 19e and 19f, which are both ends of the notch, as fulcrums. Since the lower end side of the discharge valve 9a is further bent at the valve opening fulcrum 19f, it is possible to secure a communication path in which the front side of the discharge valve presser 19 and the rear side of the discharge valve 9a communicate with each other when the discharge valve 9a is bent. .

  That is, since the exhaust port height 19h is secured inside the ring thickness 19g portion formed by the through hole 19y formed in the discharge valve retainer 19, the through hole 19y communicates with the slot 19j having the groove width 19k. A flow path is formed. Thereby, the discharge valve can be reliably operated regardless of the installation state of the vacuum pump. In addition, since the stepped portion has a shape that is cut obliquely, noise due to opening and closing of the discharge valve 9a is reduced.

  As shown in detail in FIG. 4, the drive shaft 10 and the rotating shaft 2 a of the motor 2 are connected via a shaft coupling 21. The shaft coupling 21 has a cylindrical shape, and a round hole 21a is formed on the side where the rotating shaft 2a of the motor 2 is fitted. On the other hand, the side on which the drive shaft 10 is fitted is formed with a pseudo-rectangular hole (square hole) 21b in which two surfaces of a circle are cut off. Corresponding to the square holes 21b, the drive shaft 10 is formed with fillets having planes 10b and 10c parallel to each other. A round hole 10a into which the rotation shaft of the motor can be fitted is formed at the center of the drive shaft 10.

  In the vacuum pump 1 configured as described above, the flange 5 and the dedicated sheet 17 are hermetically attached to the cylinder 4 to form the pump chamber 4b. A protrusion 4 e is formed on the surface of the cylinder 4 facing the flange 5. When the flange 5 is attached to the cylinder 4, the protrusion 4 e is crushed and the protrusion 4 e and the dedicated sheet 17 are in close contact with the flange 5. Thereby, the sealing performance of the pump chamber 4b is improved.

  When the motor shaft 2a rotates, the eccentric shaft 11 moves eccentrically, and the piston 3 attached to the outer diameter side of the eccentric shaft also moves eccentrically. At this time, the movement of the blade 3a of the piston 3 is restricted by the sliding cylinders 7a and 7b, and the rotation of the piston 3 is prevented. Note that the sliding cylinders 7a and 7b that prevent the blade 3a from rotating are made of a material and a shape (part of the cylinder) with good slidability so that the movement of the blade 3a is smooth.

  In this embodiment, the rotational driving force of the motor 2 is transmitted to the driving shaft 10 using static friction between the rotating shaft 2a of the motor and the round hole 21a. When the shaft coupling 21 rotates, a rotational force is transmitted from the square hole 21b formed in the shaft coupling 21 to the planes 10b and 10c of the fillet of the drive shaft 10, and the drive shaft 10 rotates. By the way, conventionally, the shaft coupling 21 is fixed to the shaft 10 by using a tightening screw or the like, but in this embodiment, the tightening screw or the like is not used. The reason is that if a tightening screw or the like is used, the weight of the tightening screw acts as an unbalanced load, and vibration may occur. Since no fastening screw is used, the drive shaft 10 and the shaft coupling 21 are closely fitted. In addition, since the drive shaft 10 and the shaft coupling 21 need to be disassembled, a resin such as PC (polycarbonate) is used for the shaft coupling 21 to reduce the weight and increase the friction coefficient.

  In the present embodiment, the polycarbonate shaft joint 21 is used for the above-mentioned reason, but the resin shaft joint 21 is difficult to achieve the same molding accuracy as that of a metal one. The rotation shaft 2a of the motor 2 can be inserted into the round hole 10a of the drive shaft 10 in order to prevent the coaxiality between the rotation shaft 2a of the motor 2 and the drive shaft 10 from deviating due to molding errors. As a result, it is possible to reduce vibration during high-speed rotation caused by the slight misalignment between the rotation shaft 2a of the motor 2 and the axis of the drive shaft 10, and it is possible to prevent a decrease in mechanical efficiency. Moreover, the axial length of the vacuum pump 1 can be reduced, and the vacuum pump 1 can be miniaturized.

  On the other hand, when attaching the shaft coupling 21 to the rotating shaft 2 a of the motor 2, the shaft coupling 21 can be detached from the motor 2 without using a fastening screw. For this reason, in this embodiment, a projection 21c extending in the axial direction as shown in detail in FIG. 6 is formed on the inner peripheral surface of the round hole 21a of the shaft coupling 21. A plurality of protrusions 21c are formed at intervals in the circumferential direction of the inner peripheral surface of the shaft coupling 21c. FIG. 6A is a side view of the shaft coupling 21 alone, and FIG. 6B is a cross-sectional view of the state where the shaft coupling 21 is attached to the rotating shaft 2 a of the motor 2. Since the rotating shaft 2a is inserted into the shaft coupling 21, the protrusion 21c of the resin shaft coupling 21 is elastically deformed.

  Since the plurality of protrusions 21c are formed on the inner peripheral surface of the shaft coupling 21, the rotational torque of the rotating shaft 2a of the motor 2 is reliably transmitted to the shaft coupling 21 by the frictional force. Further, due to the deformation of the protrusion 21c, the positioning of the rotating shaft 2a of the motor 2, that is, the concentricity is maintained. Further, due to the deformation of the protrusion 21c, a contact area with the rotating shaft 2a of the motor 2 necessary for torque transmission is also ensured. The height of the protrusion 21c is set so that there is no gap between the protrusion 21c and the rotation shaft 2a when the rotation shaft 2a of the motor 2 is inserted. Therefore, even if the size of the round hole 21a is slightly different or the accuracy is varied, or even if the materials of the rotary shaft 2a and the shaft coupling 21 are different and a difference in thermal deformation occurs, the distance between the protrusion 21c and the rotary shaft 2a. Since there is no gap, the rotational torque is reliably transmitted.

  Rotational torque is transmitted to the drive shaft 10 from the side surface of the square hole 21 b of the shaft coupling 21 and the parallel planes 10 b and 10 c of the fillets of the drive shaft 10. These square holes 21b and fillets are used not only for torque transmission but also for positioning during assembly. By aligning the fillet planes 10b and 10c with the two side surfaces of the square hole 21b, the shaft coupling 21 can be positioned with respect to the drive shaft 10 in the horizontal and vertical directions. Further, the rotary shaft 2 a of the motor 2 and the round hole 10 a of the drive shaft 10 can be automatically positioned by simply inserting the fillet into the square hole 21 b of the shaft coupling 21.

  FIG. 7 shows another embodiment of the shaft coupling. In the said Example, the axial coupling 21 is being fixed to the rotating shaft 2a and the drive shaft 10a with the protrusion 21c and fillet which extend in an axial direction. In the present embodiment, a plurality of softening holes 22c extending in the radial direction are formed in the shaft coupling 22 at substantially axisymmetric positions. Since the material of the shaft coupling 22 is resin, the inner peripheral surface portion of the softening hole 22c is plastically deformed inward during the processing of the softening hole 22c. Due to this deformation, when the rotary shaft 2a is inserted into the round hole 22a, the inner surface of the round hole 22a is expanded by the rotary shaft 2a, and the portion where there is no fitting gap between the rotary shaft 2a and the shaft coupling 22 is in the circumferential direction. Formed. On the drive shaft 10 side, a groove 22b extending to the outer periphery corresponding to the shape of the end of the drive shaft 10 was used instead of the pseudo square groove. By forming the shaft coupling 22 in this way, the motor shaft 2a and the drive shaft 10 can be easily positioned as in the above-described embodiment, and thermal deformation can be dealt with.

  Next, the operation of the pump unit will be described with reference to FIGS. A notch surface 10d is formed at one location on the outer periphery of the drive shaft 10 and has a truncated circular shape in cross section. Since a hole (drive shaft hole) 11a having a cross-sectional shape similar to the cross-sectional shaft shape in the notch surface 10d is formed in the eccentric shaft 11, if the drive shaft 10 is inserted into the drive shaft hole 11a, The circumferential position of the eccentric shaft 11 is positioned. When the drive shaft 10 rotates, rotational torque is transmitted from the notch surface 10d to the flat surface 11b of the drive shaft hole 11a, and the eccentric shaft 11 rotates. At this time, since the shaft center of the eccentric shaft 11 and the shaft center of the drive shaft 10 are different, the eccentric shaft 11 performs an eccentric rotational motion.

  At this time, vibration is generated in the eccentric shaft 11 due to an assembly error or a gap between the eccentric shaft 11 and the drive shaft 10, and the eccentric shaft 11 moves eccentrically, so that the vibration is amplified. As a result, the efficiency is reduced, and friction and wear of the sliding surfaces of the cylinder 4 and the piston 3 are caused. And the lifetime of the vacuum pump 1 is reduced by abrasion and thermal deformation. In order to avoid such a problem, the eccentric shaft 11 of PPS (polyphenylene sulfide) is used in this embodiment. When the eccentric shaft 11 made of PPS is used, the vacuum pump 1 can be operated with a long service life because it is lightweight and excellent in wear resistance and heat resistance and has a low coefficient of thermal expansion in the resin.

  Since the eccentric shaft 11 is lightweight, an unbalance force (centrifugal force) during rotation due to eccentricity can be reduced, and the mass of the balance weight 13 can be reduced. Thereby, a vacuum pump can be reduced in size. In this embodiment, the drive shaft 10 and the eccentric shaft 11 are fitted together, but they may be integrated by insert molding. When insert molding is performed, the drive shaft 10 is positioned in a mold, and a resin for forming an eccentric shaft is poured into the mold. If the eccentric shaft 11 is insert-molded, the concentricity with the drive shaft 10 is maintained, the performance of the compressor is improved, and the number of processing steps can be reduced.

  On the other hand, a metal material having excellent mechanical strength is used for the drive shaft 10. Since the drive shaft 10 is made of metal, the thermal expansion coefficient is different from that of the resin eccentric shaft 11. Due to this difference in thermal expansion during operation, the eccentric shaft 11 is easily displaced in the circumferential direction with respect to the drive shaft 10. Therefore, a plurality of protrusions 11c extending in the axial direction are formed on the flat surface 11b of the eccentric shaft 11. FIG. 8 is a view showing the outline of the drive shaft hole 11 a formed in the eccentric shaft 11. FIG. 4A is a contour of only the drive shaft hole 11a, and FIG. 4B is a view showing a state in which the drive shaft 10 is inserted in a cross section.

  As in the case of the rotary shaft 2a and the shaft coupling 21 of the motor 2 described above, when the drive shaft 10 is inserted into the drive shaft hole 11a, the projection 11c extending in the axial direction is elastically deformed or plastically deformed, and the drive shaft 10 And the gap between the eccentric shafts 11 is eliminated. Even if the drive shaft 10 and the eccentric shaft 11 are thermally deformed due to the heat generated by the rotational movement of the drive shaft 10, there is always no gap between the drive shaft 10 and the eccentric shaft 11 due to the deformation of the protrusion 11b. To be kept. Thereby, generation | occurrence | production of the relative displacement of the circumferential direction with respect to the drive shaft 10 of the eccentric shaft 11 can also be prevented.

  In this example, three protrusions 11c extending in the axial direction were formed on the flat surface 11b portion having a D-shaped cross section. Further, since the axial lengths of the plane 10d of the drive shaft 10 and the plane 11b of the eccentric shaft 10 are long, the planes 10d and 11b are inclined in the axial direction in consideration of assemblability and disassembly. The gradient is about 1 degree. Thus, since the vibration resulting from the clearance between the drive shaft 10 and the eccentric shaft 11 is suppressed, the weight of the balance weight 13 can be reduced.

  Next, the case where the small vacuum pump 1 mentioned above is applied to an automatic urination processing apparatus will be described below. In the automatic urine treatment apparatus, all parts including the vacuum pump 1 must be periodically replaced due to sanitary requirements. Therefore, in order to make the replacement parts recyclable, the vacuum pump 1 has a part shape that can be easily disassembled by material. Table 1 shows the results of easy assembly and disassembly and the selection of desirable materials.

  For the above reasons, stainless steel and PBT / PPS were used for the drive shaft 10 and the eccentric shaft 11, respectively. The piston 3 is made of PS / PC, which is lightweight, has high heat resistance and wear resistance, and has weak acid resistance and weak alkali resistance in chemical resistance. These materials are also rich in moldability.

  When the vacuum pump 1 is operated, each part of the vacuum pump 1 is thermally expanded. Therefore, the cylinders 4, the eccentric shaft 11, and the sliding cylinders 7 a and 7 b that guide the blade 3 a of the piston 3 are made of substantially the same material to avoid an increase in stress due to thermal expansion. In the present embodiment, the material of these parts is unified to PS (polystyrene). When the needle bearing 12 is used between the eccentric shaft 11 and the drive shaft 10 to improve the slidability, the needle shaft holding portion 3c that holds the end surface of the needle bearing 12 is formed on the eccentric shaft 11.

  Corresponding to the positions where the ball bearings 15a and 15b are held by the cylinder 4, the eccentric shaft 11 is formed with ball bearing positioning seats 11g and 11h for pressing the inner ring side of the ball bearings 15a and 15b in the axial direction. The ball bearing positioning seats 11g and 11h have a cylindrical shape and an axial length of about 0.5 mm. The axial dimension of the eccentric shaft 11 is substantially the same as the width of the piston 3 or the pump chamber 4b.

  For the cylinder 4, a material having excellent wear resistance and heat resistance, weak acid resistance and weak alkali resistance, and excellent moldability is selected. Since the cylinder 4 slides with the piston 3, PPS (polyphenylene sulfide) or PBT (polybutylene terephthalate) having a thermal expansion coefficient similar to that of the piston 3 was used in consideration of sliding characteristics with the piston 3 material. For the sliding cylinders 7 a and 7 b for guiding the blade portion 3 a of the piston 3, a material having excellent wear resistance and heat resistance and having a thermal expansion coefficient similar to that of the piston 3 is selected. In consideration of moldability, PPS or PBT was selected in this example.

  For the flange 5, a material having a high moldability and a thermal expansion coefficient similar to that of the piston 3 and the cylinder 4 is selected. Some degree of wear resistance is also required, if not as much as other sliding parts. Therefore, in this example, a homopolymer of POM (polyacetal) was selected. A POM copolymer was selected for the motor base 20 and the cover 6 in consideration of moldability.

  The size of the vacuum pump was determined based on the amount of discharged urine. The urine output of adults was determined with reference to urology bulletin 33 (4) (April 1987) 521-526, which shows the survey results of urine flow (urine output per unit time) in each age. According to this document, the maximum urine flow rate in young adults (19-39 years old) is 28.2 ± 4.6 mL per second, which is higher than any other age. Therefore, the maximum urine flow rate was set to 40 mL per second in consideration of the margin. Taking into account air entrainment and other losses, the total pumping speed of the vacuum pump was set at 70 mL per second. Therefore, for example, if the cylinder diameter is 17.2 mm, the length is 13.6 mm, and the piston diameter is 14.0 mm, the discharge amount of one rotation of the piston is about 1.066 mL, and the vacuum pump 1 is driven at 4300 rotations per minute. For example, 76.4 mL of urine can be discharged every second. Assuming about 10% loss, about 70 mL can be drained per second.

  In this embodiment, the dimensions and rotation speed of each part of the vacuum pump are determined as described above, but different dimensions and rotation speeds may be used as long as the total discharge speed satisfies 70 mL per second. Since the vacuum pump could be reduced in size and weight, the outer shape of the vacuum pump device combined with the motor could be 30 mm in diameter, 70 mm in length, and 250 g in weight. As a result, it becomes possible to use a power source such as a dry cell or a secondary cell having a voltage of about 4 to 9 V including a solar cell or a fuel cell.

  DESCRIPTION OF SYMBOLS 1 ... Vacuum pump, 1a ... Vacuum pump main body, 2 ... Motor (electric motor), 2a ... Rotary shaft, 3 ... Piston, 3a ... Blade part, 3b ... Piston outer peripheral surface, 3c ... Needle bearing holding part, 4 ... Cylinder, 4a ... Cylinder circumferential surface, 4b ... Pump chamber (Crescent space), 4c ... Discharge side casing side, 4d ... Mounting plate, 4e ... Protrusion, 4f ... Lubricant reservoir, 5 ... Flange, 5a ... Ball bearing holding Part, 5b ... lubricant reservoir, 6 ... cover, 7a, 7b ... sliding cylinder, 8 ... intake passage, 9 ... discharge passage, 9a ... discharge valve, 9b ... valve seat, 10 ... drive shaft, 10a ... Round hole, 10b, 10c ... torque transmission fillet, 10d ... notch surface, 10e ... balance weight positioning surface, 10f ... contact surface, 11 ... eccentric shaft, 11a ... drive shaft insertion hole, 11b ... eccentric shaft positioning surface, 11c ... Protrusions, 11g 11h ... Ball bearing positioning seat, 12 ... Needle bearing, 13 ... Balance weight, 13a ... Drive shaft insertion hole, 14 ... Stopper, 15a, 15b ... Ball bearing, 17 ... Dedicated seat, 19 ... Discharge valve retainer, 19a ... Valve Presser diameter, 19b ... Valve presser length, 19c ... Valve opening angle, 19d ... Discharge valve spring-up width, 19e, 19f ... Valve opening fulcrum, 19g ... Valve presser thickness, 19h ... Exhaust port height, 19i ... Hexagonal hole , 19j ... slot, 19k ... groove width, 20 ... motor base, 21 ... shaft coupling, 21a ... round hole, 21b ... (pseudo) square hole, 21c ... projection, 22 ... shaft coupling, 22a ... round hole, 22b ... Groove, 22c ... softened hole.

Claims (6)

In an automatic urination processing apparatus using a vacuum pump for sucking urine from a urine receiver, the vacuum pump is:
Made of resin, connecting the drive shaft of the vacuum pump and the motor shaft of the drive motor, forming a round hole mating with the motor shaft on one side and forming a square hole mating with the drive shaft on the other side A shaft coupling,
It is made of resin, has an outer cylindrical portion eccentric to the drive shaft, and an eccentric shaft in which the metal drive shaft is integrated by insert molding,
It is made of resin, has a plate-like blade part at the upper part of the outer periphery, the lower part has a cylindrical shape, a piston attached to the outer periphery of the eccentric shaft,
A cylinder that is made of resin, accommodates the eccentric shaft and the piston, and is disposed so that the tip of the blade portion protrudes into a space formed on the inner peripheral surface;
It is made of resin that forms a part of a cylinder, and is held by the protruding part of the cylinder that has an inner surface shape that matches the outer shape, and sandwiches the middle part of the blade part from the left and right, thereby allowing movement of the blade part. A sliding cylinder that regulates and prevents rotation of the piston;
A suction flow path and a discharge flow path that are open to a pump chamber formed between the inner peripheral surface of the cylinder and the piston;
When the motor shaft rotates, the eccentric shaft and the piston move eccentrically, and at this time, the movement of the blade is restricted by the sliding cylinder to prevent the piston from rotating, and the volume of the pump chamber Is an automatic urination treatment device characterized in that the change occurs.   2. The automatic urination processing apparatus according to claim 1, wherein the eccentric shaft, the cylinder, and the sliding cylinder are made of the same material.   2. The automatic urination treatment apparatus according to claim 1, wherein the cylinder uses PBT resin, the sliding cylinder uses PPS resin or PBT resin, and the piston uses PS resin or PC resin.   2. The automatic urination treatment apparatus according to claim 1, wherein the drive motor is driven by a dry battery or a secondary battery having an output voltage of 4 to 9V. In a vacuum pump used for aspirating urine from a urine receiver of an automatic urination processing device,
Made of resin, connecting the drive shaft of the vacuum pump and the motor shaft of the drive motor, forming a round hole mating with the motor shaft on one side and forming a square hole mating with the drive shaft on the other side A shaft coupling,
It is made of resin, has an outer cylindrical portion eccentric to the drive shaft, and an eccentric shaft in which the metal drive shaft is integrated by insert molding,
It is made of resin, has a plate-like blade part at the upper part of the outer periphery, the lower part has a cylindrical shape, a piston attached to the outer periphery of the eccentric shaft,
A cylinder that is made of resin, accommodates the eccentric shaft and the piston, and is disposed so that the tip of the blade portion protrudes into a space formed on the inner peripheral surface;
It is made of resin that forms a part of a cylinder, and is held by the protruding part of the cylinder that has an inner surface shape that matches the outer shape. A sliding cylinder that regulates and prevents rotation of the piston;
A suction flow path and a discharge flow path that are open to a crescent-shaped pump chamber formed between the inner peripheral surface of the cylinder and the piston;
When the motor shaft rotates, the eccentric shaft and the piston move eccentrically. A vacuum pump characterized by changing.   6. The vacuum pump according to claim 5, wherein the eccentric shaft, the cylinder, and the sliding cylinder are made of the same material.

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