JP2016065532A - Volumetric capacity pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable this pump to be constituted in less-expensive manner, keep high maintainability at its seal part and reduce thrust load.SOLUTION: A pump comprises a rotating shaft; an eccentric driving member having the first and second disc members; the first cylinder; the second cylinder; a pump head having a suction port for feeding fluid and a discharging port for discharging fluid; and a cylindrical member having an eccentric shaft connected to the extremity end of the rotating shaft in such a manner that a position in a rotating shaft direction can be adjusted and a bearing part in it, each of the disc members comprises an eccentric shaft unit having the first position setting part installed at an outer peripheral side for defining a position of the second disc member in a direction of rotating shaft at an outer peripheral side; a fixing member connected to the extremity end of the eccentric shaft unit in such a manner that a position in a rotating shaft direction can be adjusted for defining a position in a direction of rotating shaft of the first disc member; and a cylindrical resilient member arranged to shut off the extremity end of the rotating shaft and a base end side of the cylindrical member of the eccentric shaft unit against fluid within the pump head.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a positive displacement pump that sucks and discharges fluid by changing the volume of a pump chamber using an eccentric drive member.

  A positive displacement pump that sucks and discharges fluid by changing its volume sucks fluid from the suction port while increasing the volume of the pump chamber, and discharges fluid from the discharge port while decreasing the volume of the pump chamber. As one of such positive displacement pumps, an arc-shaped pump chamber is divided into an inner pump chamber and an outer pump chamber by an arc-shaped partition formed on an eccentric disk (eccentric drive member). There is known a positive displacement pump using an eccentric disk that realizes a discharge flow rate substantially free of pulsation by shifting the phase of the change in the discharge flow rate by 180 ° (Non-Patent Document 1).

http://www.psgdover.com/en/mouvex/mouvexproducts/eccentric-disc-pumpsmouvex-technology/a-series-pumps

  However, the above-described positive displacement pump of the prior art has a problem in durability because a thrust load is applied by the pressure in the pump chamber. There is also a desire to reduce costs by reducing the number of pump parts, and in particular to improve the maintainability of the seal portion.

  The present invention has been made in view of such problems, and an object thereof is to provide a positive displacement pump that can be configured at low cost, has high maintainability of a seal portion, and can reduce a thrust load.

  The positive displacement pump according to the present invention has a rotation shaft and is eccentrically mounted on the rotation shaft, and moves along an annular path centering on the rotation shaft as the rotation shaft rotates. And an eccentric drive member having a first disk member and a second disk member, which are coaxially arranged independently of each other, and the first disk member so as to face the first disk member from one side in the rotation axis direction. A first cylinder forming an annular or arc-shaped first pump chamber together with one disk member, and the second disk member arranged to face the second disk member from the other side in the rotation axis direction. A second cylinder that forms an annular or arcuate second pump chamber together with the disk member, a suction port for introducing fluid into the first pump chamber and the second pump chamber, the first and second Pump room or A pump head having a discharge port for discharging a fluid, an eccentric shaft coupled to a tip of the rotating shaft so as to adjust the position of the rotating shaft, and an outer cylindrical member having a bearing portion therein; An eccentric shaft unit having two first disk members mounted on the outer peripheral side and having a first positioning portion defining a position of the second disk member in the rotational axis direction on the outer peripheral side; and a tip of the eccentric shaft unit A mounting member having a second positioning portion that is coupled so as to be positionally adjustable in the direction of the rotation axis and that defines a position of the first disk member in the direction of the rotation axis; and a front end side of the rotation shaft and the cylinder of the eccentric shaft unit And a cylindrical elastic member arranged so as to cut off the base end side of the cylindrical member from the fluid in the pump head.

  According to the positive displacement pump according to the present invention, the first and second pump chambers are formed on both sides of the first and second disk members of the eccentric drive member in the rotation axis direction. The thrust load to be generated is in the opposite direction and is just offset, so that the generation of the thrust load can be reduced. Thereby, since it becomes possible to maintain a non-sliding state between the 1st and 2nd disk members and the 1st and 2nd cylinders, generation of contamination can be prevented.

  In addition, since the first and second disk members are independently coaxially arranged so that their positions can be adjusted independently, the first and second disk members and cylinders can be managed without strictly managing the processing accuracy and assembly accuracy of the disk members and cylinders. The disk members can be independently or automatically adjusted in position. For this reason, compared with the case where both are integral types, processing precision management and assembly precision management become easy, and it becomes possible to manufacture a positive displacement pump more cheaply and easily.

  In addition, each disk member can be individually adjusted and assembled in the direction of the rotation axis by the eccentric shaft unit and the first and second positioning portions of the mounting member, so that clearance management that matches the characteristics of the fluid to be transferred Therefore, a positive displacement pump with higher pump efficiency can be provided.

  Further, since the distal end side of the rotary shaft and the proximal end side of the cylindrical member of the eccentric shaft unit are shielded from the fluid in the pump head by the cylindrical elastic member, a seal that eliminates the need for mounting a mechanical seal on the rotary shaft A less structure is realized, and it is possible to improve the maintainability by reducing the number of parts related to the seal.

  In one embodiment of the present invention, the first and second disk members are arranged coaxially via an annular elastic member that imparts a predetermined repulsive force therebetween.

  In another embodiment of the present invention, the cylindrical elastic member is made of a boot made of a flexible material, or a bellows made of a resin material or a metal material.

  According to the present invention, it can be configured at low cost, the maintainability of the seal portion is high, and the thrust load can be reduced.

It is a front view which permeate | transmits and shows a part of positive displacement pump which concerns on the 1st Embodiment of this invention. It is sectional drawing which looked at the same volume type pump from the side surface direction. It is a disassembled perspective view of the positive displacement pump. It is side sectional drawing of the eccentric drive member of the positive displacement pump. It is a rear view of the 2nd disk member of the same volume type pump. It is sectional drawing which looked at the positive displacement pump which concerns on the 2nd Embodiment of this invention from the side surface direction. It is side sectional drawing of the eccentric drive member of the positive displacement pump. It is a rear view of the 2nd disk member of the same volume type pump.

  Hereinafter, a positive displacement pump according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.

[First Embodiment]
FIG. 1 is a front view showing a part of the positive displacement pump according to the first embodiment of the present invention, and FIG. 2 is a cross-sectional view of the positive displacement pump as viewed from the side. FIG. 3 is an exploded perspective view of the same displacement pump, and FIG. 4 is a side sectional view of an eccentric drive member of the same displacement pump. FIG. 5 is a rear view of the second disk member of the same displacement pump.

  As shown in FIGS. 1 to 4, the positive displacement pump 100 according to the first embodiment transmits a rotational driving force around a rotating shaft 18 that transmits a rotational driving force from a rotational driving source such as a motor (not shown). Part 1 is provided. In addition, the positive displacement pump 100 is attached to the rotary shaft 18 of the rotational driving force transmission unit 1 in an eccentric state, and is independently formed and combined with each other in the direction of the rotary shaft. An eccentric drive member 2 having a member 25 is provided.

  Further, the positive displacement pump 100 is opposed to the front side in the rotation axis direction of the first disk member 24 of the eccentric drive member 2, is supplied with fluid from the first flow path, and is first with the first disk member 24. The first pump head 3 forming the pump chamber 6 is provided. The positive displacement pump 100 is opposed to the second disk member 25 of the eccentric drive member 2 from the rear side in the rotation axis direction, is supplied with fluid from the second flow path, and is supplied with the second disk member 25 together with the second disk member 25. The second pump head 4 forming the pump chamber 7 is provided.

  The positive displacement pump 100 further includes a cylindrical third pump head 5 that is sandwiched between the first pump head 3 and the second pump head 4 and accommodates the eccentric drive member 2 therein. These first to third pump heads 3 to 5 are fixed to each other by a bolt 61 shown in FIG. Further, the rotational driving force transmission unit 1 is fixed to the second pump head 4 by a bolt 62. The opening on the front side of the first pump head 3 is covered with a front cover 34.

  The rotational driving force transmission unit 1 includes a rotation shaft 18 and a bearing portion 17 that rotatably supports the rotation shaft 18. The bearing portion 17 is composed of a pair of tapered roller bearings 171 and 172 that are arranged in plane symmetry to receive loads in the radial direction and the thrust direction (axial direction). These tapered roller bearings 171 and 172 are accommodated in a cylindrical bearing casing 122 and the inside is sealed by seal members 173 and 174 disposed at both ends.

  A flange 121 is integrally formed on the front end side of the bearing casing 122, and is fixed to the second pump head 4 via a joint 121a. Further, an attachment portion 13 for attaching the positive displacement pump 100 to a fixing portion such as a floor surface or a wall surface is fixed to the bearing casing 122 and the first pump head 3 by bolts 63.

  An eccentric shaft unit 15 having an eccentric shaft 15 a that is eccentric with respect to the rotating shaft 18 is attached to a portion of the rotating shaft 18 that is disposed inside the first to third pump heads 3 to 5. A bearing 16 such as a ball bearing is attached to the eccentric shaft 15a. The bearing 16 is fixed to the eccentric shaft 15a by an outer cylindrical member 15A mounted on the outside thereof and a bearing fixing portion 16a attached to the base end side thereof.

  The first and second disk members 24 and 25 of the eccentric drive member 2 are mounted on an outer cylindrical member 15A mounted on the outer side of the eccentric shaft 15a of the eccentric shaft unit 15. That is, the disk members 24 and 25 are rotatably mounted on the eccentric shaft 15 a via the bearing 16. Thereby, the eccentric drive member 2 moves along an annular path centering on the rotation shaft 18 as the rotation shaft 18 rotates.

  As shown in FIG. 2, the drive system of the rotary shaft 18 and the eccentric shaft 15 a of the positive displacement pump 100 includes, for example, a drive-side rotary shaft portion 180 that transmits a rotation operation, and a rotary shaft on the tip side of the drive-side rotary shaft portion 180. A front end side rotating shaft portion 181 which is integrally formed on the front end side and an eccentric shaft 15a is integrally formed on the front end side, and the position of the rotating shaft direction can be adjusted with respect to the driving side rotating shaft portion 180; A cap member (attachment member) 191 that is coupled from the rotation axis direction and can adjust the position of the eccentric shaft unit 15 in the rotation axis direction.

  The drive-side rotating shaft portion 180 is a hollow shaft that transmits a rotational driving force from a rotational driving source such as a motor (not shown), and is rotatably supported by the bearing portion 17 described above. There are first to third pump heads at the connecting portion of the drive side rotary shaft portion 180 and the eccentric shaft unit 15, that is, at the distal end side of the rotary shaft 18 and the proximal end side of the outer cylindrical member 15 A of the eccentric shaft unit 15. 3 to 5, for example, the cylindrical elastic member 11 disposed so as to block the distal end side of the rotary shaft 18 and the distal end side rotary shaft portion 181 from the fluid together with the outer cylindrical member 15A is mounted.

  The cylindrical elastic member 11 is made of a boot made of a flexible material such as rubber or a bellows made of a resin material or a metal material in order to absorb the eccentric motion. This cylindrical elastic member 11 realizes a sealless structure that eliminates the need for mounting a mechanical seal on the drive-side rotating shaft portion 180. A front portion of the drive side rotation shaft portion 180 is formed in a substantially cylindrical shape, and a front end side rotation shaft portion 181 is slidably inserted into the front portion.

  The cylindrical elastic member 11 is mounted in a liquid-tight manner between the rear end side and the bush 329 attached to the joint 121a, and the distal end side is attached to the outer cylindrical member 15A of the eccentric shaft unit 15 and the proximal end side thereof. By mounting in a liquid-tight manner between the mounting nut portion 319 and the mounting nut portion 319, the mounting nut portion 319 is disposed so as to surround the coupling portion.

  The distal end side rotation shaft portion 181 is a substantially partially cylindrical part columnar member coaxial with the distal end portion of the drive side rotation shaft portion 180. A part of the outer cylindrical member 15A of the eccentric shaft unit 15 is formed with a step protruding in the outer circumferential direction with respect to the rotary shaft 18, and is in contact with the step 250a provided in the insertion hole 250 of the second disk member 25. In this manner, a positioning portion 182 for positioning the second disk member 25 in the rotation axis direction is formed.

  Further, the cylindrical portion of the distal end side rotating shaft portion 181 is divided into a plurality of segments 184 by a plurality of slits 183, and constitutes a collet chuck together with a collet 186 formed integrally with a stud bolt 188 and tapered. doing. A bolt insertion hole 187 that penetrates along the rotation shaft 18 is formed in the drive side rotation shaft portion 180, and the stud bolt 188 can be operated from the base end side of the drive side rotation shaft portion 180.

  The cap member 191 is a cap that is inserted into the front portion of the outer cylindrical member 15A of the eccentric shaft unit 15 from the front. Further, the rear end of the cap member 191 forms a step protruding in the outer peripheral direction with respect to the outer peripheral surface of the outer cylindrical member 15A, and comes into contact with the front surface of the first disk member 24, thereby the first disk member. A positioning portion 192 for positioning in the rotation axis direction of 24 is formed.

  The distal end portion of the outer cylindrical member 15A of the eccentric shaft unit 15 is divided into a plurality of segments 194 by a plurality of slits 193, and is colleted together with a collet 196 that is integrally attached to the stud bolt 198 and formed in a tapered shape. It constitutes the chuck. The cap member 191 is formed with a bolt operation hole 197 penetrating along the eccentric shaft 15a, so that the stud bolt 198 can be operated from the distal end side of the cap member 191.

  As shown in FIG. 4, the eccentric drive member 2 includes a first disk member 24 and a second disk member 25 that are independently formed. The first and second disk members 24 and 25 are configured to be able to adjust the position in the rotation axis direction with respect to the rotation shaft 18 and the eccentric shaft 15a.

  At the center of the first and second disk members 24, 25, these disk members 24, 25 are attached to the outer cylindrical member 15 A of the eccentric shaft unit 15 and mounted on the eccentric shaft 15 a via the bearing 16. Insertion holes 240 and 250 are respectively formed. The first and second disk members 24 and 25 are provided with coupling base portions 201 and 206 projecting from the opposing surfaces, and the opposing surfaces 24a and 25a of the coupling base portions 201 and 206 are projected. The disk members 24 and 25 are arranged so that they face each other with a slight gap.

  The coupling base portion 206 of the second disk member 25 is formed with an annular groove portion 25b that opens toward the facing surface 25a, and an O-ring 25c as an annular elastic member is coaxially disposed in the groove portion 25b. Yes. The depth of the groove portion 25b in the rotation axis direction is, for example, an intermediate value between the depth defined when the O-ring 25c is used as a gasket and the depth defined when used for movement / fixing, or a value close thereto. Is set to

  The O-ring 25c is configured to have an elastic modulus capable of applying a predetermined repulsive force between the first and second disk members 24, 25. Thus, each of the disk members 24 and 25 has a repulsive force between the surfaces of the disk members 24 and 25 for adjusting the clearance between the first and second cylinders 312 and 412 of the eccentric drive member 2 (clearance adjustment). It becomes possible to seal between the disk members 24 and 25.

  Since the first and second disk members 24 and 25 are coaxially arranged via the O-ring 25c, there is a concern that slight backlash occurs in the rotation direction. However, since the first and second disk members 24 and 25 are substantially fixed by an appropriate repulsive force and frictional force of the O-ring 25c, these angles do not shift during the operation of the pump.

  The axially outer surfaces of the first and second disk members 24 and 25 form a first pump chamber 6 and a second pump chamber 7 together with a first cylinder 312 and a second cylinder 412 described later, respectively. It functions as pump chamber forming surfaces 243, 244, 253, 254. Further, the first and second disk members 24, 25 have C-shaped or arc-shaped first partition walls 242 disposed on the outer surfaces in the axial direction of the first and second disk members 24, 25 with the positions of the open ends thereof being shifted by 180 °, respectively. Each of the second partition walls 252 protrudes outward in the axial direction.

  The first and second partition walls 242 and 252 have diameters that can move along an annular path accommodated in the first and second cylinders 312 and 412 and regulated by an eccentric amount, and the insertion holes 240 and 250. And is formed coaxially.

  The first and second disk members 24 and 25 are respectively provided with disk members 24 and 25 at radially inner positions of the partition walls 242 and 252 near the open ends of the first and second partition walls 242 and 252, respectively. Penetrating pump chamber outlets 245 and 255 are formed, respectively. The pump chamber discharge port 245 formed in the first disk member 24 and the pump chamber discharge port 255 formed in the second disk member 25 are also formed at positions shifted from each other by 180 °.

  The first pump head 3 includes a first frame 31 and a second frame 32 (see FIGS. 2 and 3). The first frame 31 has a cap member accommodating port 311 for accommodating the cap member 191 in the center, and a first partition 242 is accommodated outside the first frame 31, and the C-shaped or arc-shaped first pump chamber 6. A first cylinder 312 is formed.

  Further, an opposing surface 314 facing the pump chamber forming surface 244 is formed on the outer periphery thereof, and an outer peripheral flange 315 is formed on the outer side thereof. A frame portion 313 between the cap member accommodation port 311 and the first cylinder 312 is coupled to the facing surface 314 of the first frame 31 through a connecting portion (not shown) provided in a part. Note that the position of the connecting portion corresponds to the position of the open end of the first partition 242 of the first disk member 24.

  A suction port 322 that penetrates the first frame 31 is formed in the vicinity of the connecting portion on the pump chamber forming surface that forms the first pump chamber 6 of the first frame 31. The suction port 322 and the pump chamber discharge port 245 of the first disk member 24 are arranged on opposite sides with respect to the connecting portion.

  Further, a suction port that penetrates the second frame 32 and communicates with the first fluid flow path 321 at a position corresponding to the suction port 322 of the first frame 31 and the rotation axis direction in the second frame 32. 322a is formed. A first fluid suction port 512 for introducing a fluid to be transferred (transfer fluid such as liquid or gas) is formed at the upper end of the first fluid channel 321.

  The second pump head 4 is configured in substantially the same manner except for a part thereof except that the positional relationship with the first pump head 3 described above is 180 ° different. That is, the second pump head 4 includes a third frame 41. The third frame 41 has a cylindrical member accommodation port 411 that penetrates the third frame 41 in the center and accommodates the outer cylindrical member 15A of the eccentric shaft unit 15, and the second partition 252 on the outer side thereof. Is formed, and a second cylinder 412 forming a C-shaped or arc-shaped second pump chamber 7 is formed.

  Further, an opposing surface 415 facing the pump chamber forming surface 254 is formed on the outer periphery thereof, and an outer peripheral flange 410 is formed on the outer side thereof. A frame portion 413 between the cylindrical member accommodation port 411 and the second cylinder 412 is coupled to the facing surface 415 of the third frame 41 via a connecting portion (not shown) provided in a part. Note that the position of the connecting portion corresponds to the position of the open end of the second partition 252 of the second disk member 25.

  A suction port 417 that penetrates through the third frame 41 is formed in the vicinity of the connecting portion on the pump chamber forming surface that forms the second pump chamber 7 of the third frame 41. The suction port 417 and the pump chamber discharge port 255 of the second disk member 25 are disposed on the opposite sides with respect to the connecting portion.

  A second fluid channel 416 is formed in the fourth frame 42, and the second fluid channel 416 communicates with the suction port 417 of the third frame 41 in the rotation axis direction. The second fluid channel 416 forms an accommodation space for the cylindrical elastic member 11 in the center of the fourth frame 41. The second fluid channel 416 also communicates with the cylindrical member accommodation port 411, and a second fluid suction port 513 for introducing the fluid to be transferred is formed at the upper end thereof.

  The third pump head 5 is disposed between the first frame 31 and the third frame 41. The space in which the eccentric drive member 2 of the third pump head 5 is accommodated constitutes a discharge fluid flow path 511 in which the transfer fluid discharged from the first and second pump chambers 6 and 7 is accommodated. A fluid discharge port 514 that communicates with the discharge fluid channel 511 and discharges the transfer fluid to the outside is formed at the lower end of the third pump head 5.

  In the positive displacement pump 100 configured as described above, when a rotational driving force is applied to the driving side rotational shaft portion 180 of the rotational shaft 18 by a rotational driving source such as a motor, the rotational motion is transmitted to the eccentric shaft 15a, and the eccentric shaft unit. The eccentric drive member 2 attached to the motor 15 moves so as to move along an annular path having a radius corresponding to the amount of eccentricity centered on the central axis of the rotation shaft 18. Since the eccentric drive member 2 is rotatably mounted to the eccentric shaft 15a via the outer cylindrical member 15A of the eccentric shaft unit 15 and the bearing 16, the rotation of the eccentric drive member 2 itself is restricted. Together with the above, it moves in parallel along the circular path. The parallel movement for one rotation along this circular orbit is one cycle of the positive displacement pump 100.

  In the positive displacement pump 100, the flow rate change in the first pump chamber 6 and the flow rate change in the second pump chamber 7 are in a phase different by 180 °. Therefore, by adding the flow rate from the first pump chamber 6 and the flow rate from the second pump chamber 7, it is possible to realize supply of fluid without pulsation.

  In the positive displacement pump 100, the suction is always performed by the first and second pump chambers 6, 7, and the force generated by the suction of the first pump chamber 6 and the suction of the second pump chamber 7 are generated. The force is in the opposite direction. Therefore, it is possible to reduce the load in the axial direction of the crankshaft (rotating shaft 18) and reduce the burden on the tapered roller bearings 171 and 172 (bearings) of the bearing portion 17.

  For this reason, it is possible to apply a small bearing as the tapered roller bearings 171 and 172, and the pump chamber can be maintained in a substantially non-sliding state. Can be suppressed. Further, since the rotation direction can be reversed as a matter of course, the suction and discharge is reversed when the rotation is reversed.

  In the positive displacement pump 100 according to the present embodiment, it is possible to adjust the positions of the first and second disk members 24 and 25 of the eccentric drive member 2 in the rotation axis direction. First, after inserting the stud bolt 188 from the distal end side into the bolt insertion hole 187 of the drive side rotational shaft portion 180 of the rotational driving force transmitting portion 1, the distal end side rotational shaft portion 181 of the eccentric shaft unit 15 is set, and the joint 121a The bushing 329 and the mounting nut portion 319 are attached, and the cylindrical elastic member 11 is mounted.

  Next, the second pump head 4 is attached to the bearing casing 122, the second disk member 25 is placed on the outer cylindrical member 15 </ b> A of the eccentric shaft unit 15, and the step 250 a of the second disk member 25 is placed on the positioning portion 182. Install firmly so that it touches. Then, in a state in which a target clearance is secured in advance between the second disk member 25 and the second pump head 4, the stud is inserted from the base end side of the drive side rotating shaft portion 180 through the bolt insertion hole 187. The bolt 188 is rotated, thereby pressing the collet 186 forward.

  As a result, the segment 184 is pressed in the outer circumferential direction by the side surface of the collet 186 that is integrally attached to the stud bolt 188 and formed in a tapered shape, so that the front end side rotating shaft portion 181 and the front end portion of the driving side rotating shaft portion 180 are The positional relationship is fixed. In order to set the clearance, for example, a spacer of several tens of μm is inserted between the front surface of the facing surface 415 of the second pump head 4 and the pump chamber forming surface 254 of the second disk member 25, and the stud bolt After the positioning by 188, the second disk member 25 may be pulled forward slightly to remove the spacer.

  In addition, when the front end side rotary shaft portion 181 is set in the front portion of the drive side rotary shaft portion 180, the collet 186 is pressed and tightened to some extent by the stud bolt 188 in advance and the front end side rotary shaft portion is fixed before the positional relationship is fixed. The frictional force with respect to the drive-side rotating shaft 180 of 181 may be adjusted.

  Next, the O-ring 25c is attached to the groove 25b of the second disk member 25, and the first disk member 24 is attached to the front portion of the second disk member 25 of the outer cylindrical member 15A of the eccentric shaft unit 15. Assemble. Then, the stud bolt 198 and the cap member 191 are mounted on the front side of the eccentric shaft unit 15 so that the positioning portion 192 at the rear end of the cap member 191 is firmly in contact with the front surface of the first disk member 24.

  Thereafter, the first disk member 24 and the second disk member 25 have a slight clearance due to, for example, the crushing condition of the O-ring 25c, and the bolt operation hole 197 is inserted from the front end side of the cap member 191. Then, the stud bolt 198 is rotated, and thereby the collet 196 is pushed backward. As a result, the segment 194 is pressed in the outer circumferential direction by the side surface of the tapered collet 196 that is integrally attached to the stud bolt 198, and the positional relationship between the cap member 191 and the front end portion of the eccentric shaft unit 15 is fixed. The

  And the 3rd pump head 5 and the 1st pump head 3 are attached to the 2nd pump head 4, and the positive displacement pump 100 is comprised. The clearance between the first disk member 24 and the first frame 31 can be adjusted by attaching the stud bolt 198 via the cap member receiving port 311 before attaching the front cover 34 without using the spacer as described above. By operating it, it is possible to carry out easily even after the pump is assembled.

  By doing so, the clearance between the first disk member 24 and the first frame 31 and the clearance between the second disk member 25 and the third frame 41 can be suitably adjusted. In the positive displacement pump 100 of the embodiment, the clearance between the eccentric drive member 2 and each of the pump heads 3 and 4 is automatically adjusted by the elastic repulsion force of the O-ring 25c, etc., without adjusting various clearances so severely. It has a structure that can be adjusted to the optimum state.

  The clearance (interval) between the first and second disk members 24 and 25 and the first and second cylinders 312 and 412 in the positive displacement pump 100 greatly affects the transfer performance of the pump. For example, if this interval is too wide, the transfer capability may be reduced. On the other hand, if this interval is too narrow, the first and second disk members 24 and 25 slide on the first and second cylinders 312 and 412, and the coefficient of friction between them increases, resulting in an eccentric drive member. The movement of 2 may be hindered, leading to a decrease in transfer capability, and contamination may occur at the sliding portion.

  Depending on the conditions for driving the positive displacement pump 100, a suitable distance between the first and second disk members 24 and 25 and the first and second cylinders 312 and 412 may change. For example, when the positive displacement pump 100 is operated at a high temperature, it is necessary to consider the thermal expansion of the eccentric drive member 2, and when the transfer fluid is a liquid, a suitable interval is also determined by the viscosity of the liquid. Will be different.

  In this regard, in the positive displacement pump 100 according to the present embodiment, the first disk member 24 and the second disk member are adjusted by the position adjustment of the positioning portions 182 and 192 in the rotation axis direction and the elastic repulsive force of the O-ring 25c. It is possible to adjust the distance between the first and second cylinders 312 and 412 of the eccentric drive member 2 and the distance between the first and second cylinders 312 and 412. Therefore, it is possible to provide a highly versatile positive displacement pump capable of suitably adjusting these intervals according to conditions.

  Further, since the cylindrical elastic member 11 and the outer cylindrical member 15A are configured to cut off the distal end side of the rotary shaft 18 and the distal end side rotary shaft portion 181 from fluid, the drive side rotary shaft of the rotary shaft 18 is configured. There is no need to attach a mechanical seal to the portion 180 as in the prior art, and it is possible to realize a sealless structure and improve maintenance while reducing costs.

  In particular, in a structure such as a mechanical seal, a lubrication structure is essential for the sliding portion, which is not suitable for high viscosity liquids and the like. If it cuts off with the cylindrical elastic member 11 like the positive displacement pump 100, the structure is simple and maintenance such as cleaning becomes easy. In addition, you may comprise so that a lubrication structure may be provided in the inside of the cylindrical elastic member 11. FIG.

[Second Embodiment]
Next, the positive displacement pump according to the second embodiment will be described. FIG. 6 is a cross-sectional view of the positive displacement pump according to the second embodiment of the present invention as viewed from the side. FIG. 7 is a side sectional view of the eccentric drive member of the same displacement pump. FIG. 8 is a rear view of the second disk member of the same displacement pump.

  As shown in FIGS. 6 to 8, the positive displacement pump 101 according to the second embodiment is different from the first embodiment in that the eccentric drive member 2 is composed of the first and second disk members 24 and 25. However, the first and second disk members 24 and 25 are coupled differently. The other points are configured similarly.

  That is, the coupling bases 201 and 206 are opposed to the first and second disk members 24 and 25 of the eccentric drive member 2 of the positive displacement pump 100 with a predetermined gap therebetween. The coupling base portion 206 formed on the front surface of the second disk member 25 has a guide pin locking hole 207 that opens to the opposite surface 25 a side to lock the guide pin 26 and a spring lock that locks the spring 27. A blind hole 208 is formed.

  In addition, the coupling base portion 201 formed on the back surface of the first disk member 24 also engages the spring 27 with the guide pin locking hole 202 that opens to the facing surface 24a side and locks the guide pin 26. A spring locking hole 203 is formed. Here, the inner diameter of the guide pin locking hole 202 is formed larger than the outer diameter of the guide pin 26. It should be noted that the spring locking holes 203 and 208 and the guide pin locking holes 202 and 207 are provided approximately equally from the centers of the insertion holes 240 and 250 at predetermined angles, respectively.

  That is, the first disk member 24 and the second disk member 25 of the eccentric drive member 2 according to the second embodiment have a so-called backlash with respect to the rotation direction, and are independent in a predetermined angle range, for example. And has a rotatable structure. The angles of the first and second disk members 24 and 25 are adjusted to a naturally suitable position during the operation of the pump.

  In the positive displacement pump 101 according to the second embodiment configured as described above, the first and second disk members 24 and 25 of the eccentric drive member 2 are loosely coupled. It is possible to increase the tolerance for. That is, since the first and second disk members 24 and 25 are configured to be independently rotatable within a predetermined angle range, the first and second cylinders 312 and 412 of both the disk members 24 and 25 are configured. The rotation angle with respect to is suitably adjusted during operation. Therefore, the eccentric drive member 2 of the present embodiment does not need to precisely adjust the rotation angle of the disk members 24 and 25 with respect to each other, and can be easily manufactured.

  In the positive displacement pumps 100 and 101 according to the first and second embodiments described above, the discharge flow rates of the first pump chamber 6 and the second pump chamber 7 are opposite to each other, that is, the first of the eccentric drive member 2. Although the first and second disk members 24 and 25 are configured to be in reverse phase, the first and second disk members 24 and 25 are configured so that the discharge flow rates of the pump chambers 6 and 7 are in phase. The eccentric drive member 2 may be configured by arranging 25 in phase. In this case, the pump may be formed so that the suction ports 322 and 417 are both positioned below the rotary shaft 18, for example.

DESCRIPTION OF SYMBOLS 1 Rotation driving force transmission part 2 Eccentric drive member 3 1st pump head 4 2nd pump head 5 3rd pump head 6 1st pump chamber 7 2nd pump chamber 11 Cylindrical elastic member 15 Eccentric shaft unit 15A Outer cylindrical member 15a Eccentric shaft 18 Rotating shaft 24 First disk member 25 Second disk member 25c O-ring 180 Drive-side rotating shaft portion 181 Tip-side rotating shaft portion 182 Positioning portion 191 Cap member 192 Positioning portion 312 First Cylinder 412 Second cylinder

Claims (3)

A rotation axis;
A first disk that is eccentrically mounted on the rotating shaft and moves along an annular path centering on the rotating shaft as the rotating shaft rotates, and is coaxially arranged in an independent state so that the respective positions can be adjusted. An eccentric drive member having a member and a second disk member;
A first cylinder that is disposed so as to face the first disk member from one side in the direction of the rotation axis and forms an annular or arc-shaped first pump chamber together with the first disk member;
A second cylinder that is disposed so as to face the second disk member from the other side in the rotation axis direction and forms a second pump chamber having an annular shape or an arc shape together with the second disk member;
A pump head having a suction port for introducing fluid into the first pump chamber and the second pump chamber, and a discharge port for discharging fluid from the first and second pump chambers;
The rotating shaft includes a cylindrical member having an eccentric shaft and a bearing portion that are coupled to the tip of the rotating shaft so that the position of the rotating shaft can be adjusted. The first and second disk members are mounted on the outer peripheral side, and An eccentric shaft unit having a first positioning portion for defining a position of the second disk member in the rotation axis direction on the outer peripheral side;
An attachment member having a second positioning portion that is coupled to the tip of the eccentric shaft unit so that the position of the first disk member in the rotation axis direction can be adjusted;
A volume comprising: a cylindrical elastic member arranged so as to cut off the distal end side of the rotating shaft and the proximal end side of the cylindrical member of the eccentric shaft unit from the fluid in the pump head. Type pump. The positive displacement pump according to claim 1, wherein the first and second disk members are arranged coaxially via an annular elastic member that imparts a predetermined repulsive force therebetween. The positive displacement pump according to claim 1 or 2, wherein the cylindrical elastic member is made of a boot made of a flexible material, or a bellows made of a resin material or a metal material.

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