KR100743693B1 - Reciprocating pump and check valve - Google Patents

Abstract

In a reciprocating pump, drive power of a drive-power supply member is transmitted to a diaphragm within a diaphragm drive chamber via operating fluid. An operating-fluid-flow regulation chamber for regulating the flow of operating fluid is located between the drive-power supply member and the diaphragm drive chamber. A first gas discharge member and a second gas discharge member are respectively located in an upper part of the inside of the operating-fluid-flow regulation chamber and an upper part of the inside of the diaphragm drive chamber. The first gas discharge member is held in fluid communication with the second gas discharge member so as to constitute a single gas discharge mechanism. This single gas discharge mechanism is provided with a reverse-flow prevention member for preventing a reverse flow of fluid from the first gas discharge member to the second gas discharge member.

Description

Reciprocating pump and backflow preventer {RECIPROCATING PUMP AND CHECK VALVE}

1 is a schematic cross-sectional view of a reciprocating pump according to an embodiment of the present invention.

FIG. 2 is a II-II cross-sectional view of FIG. 1.

3 is an enlarged view of a fluid conveying part that constitutes the reciprocating pump according to the present embodiment.

4 is an enlarged view of the gas discharge mechanism that constitutes the reciprocating pump according to the present embodiment.

5A and 5B are enlarged views of the auxiliary plunger mechanism that constitutes the reciprocating pump according to the present embodiment, and each shows the start of driving and the end of driving of the auxiliary plunger.

6A and 6B are enlarged views of the auxiliary plunger mechanism when the flow rate of the auxiliary plunger constituting the reciprocating pump according to the present embodiment is set to 0, and the start and end of the drive of the auxiliary plunger are shown, respectively.

7 is an enlarged view of a gas discharge mechanism that forms a reciprocating pump according to another embodiment.

8 is an enlarged view of a gas discharge mechanism that forms a reciprocating pump according to another embodiment.

9A and 9B are schematic cross-sectional views showing a first embodiment of the non-return plate according to the embodiment of the present invention.

10 is a schematic cross-sectional view showing a second embodiment of the backflow prevention plate according to the embodiment of the present invention.

 It is a schematic sectional drawing which shows 3rd Embodiment of the backflow prevention board which concerns on embodiment of this invention.

12 is an external front view of a reciprocating pump according to another embodiment of the present invention.

It is an external side view of the reciprocating pump shown in FIG.

FIG. 14 is a schematic A-A cross section of FIG. 12.

FIG. 15 is a schematic cross-sectional view taken along the line BB of FIG. 13. FIG.

FIG. 16 shows pressure waveforms in each diaphragm of the reciprocating pump shown in FIG. 12 and the like, FIG. 16A shows pressure waveforms in the diaphragm, FIG. 16B shows pressure waveforms in the auxiliary diaphragm, and FIG. 16c shows that these waveforms were polymerized.

17 is a partial cross-sectional view of a reciprocating pump according to another embodiment of the present invention.

TECHNICAL FIELD The present invention relates to a reciprocating pump and a backflow preventing plate, and more particularly, to a reciprocating pump configured to properly discharge gas in a pump and a backflow preventing plate used for the reciprocating pump.

BACKGROUND ART A reciprocating pump for conveying a fluid by driving a diaphragm is known in the art and generally converts a rotational motion obtained by a driving means such as a motor into a linear reciprocating motion via a cam. It is configured to drive the diaphragm by movement. Moreover, as a more specific structure, the structure which transmits the linear reciprocation movement based on a motor etc. to the diaphragm via the hydraulic fluid which is a working medium is known.

In the reciprocating pump configured as described above, an elastically deformable diaphragm is reciprocated using operating oil, and suction and discharge of the conveying fluid are performed by the reciprocating motion of the diaphragm. Therefore, such a diaphragm is formed relatively thinly based on the necessity of this elastic deformation and reciprocation motion.

Since the reciprocating pump according to the prior art is configured using a diaphragm formed relatively thin as described above, when the diaphragm is overloaded, there is a fear that the diaphragm may be deformed or cracked.

As a reciprocating pump provided with a technique for preventing deformation or cracking of such a diaphragm, for example, a pump disclosed in Japanese Patent Application Laid-Open No. 61-61990 (Reference 1) is known. In the reciprocating pump disclosed herein, a plate unit operating together with the diaphragm is provided, and the plate unit limits the movement of the diaphragm and controls the inflow state of the hydraulic oil before the overload acts on the diaphragm. It is.

Moreover, in the fluid conveyance path | route by a prior art, the backflow prevention plate comprised with the ball etc. is used in order to prevent the backflow of conveying fluid. In particular, when conveying a highly viscous fluid (adhesive liquid), since the passage is reliably closed, for example, as described in Japanese Patent Application Laid-Open No. 2000-356274 (Ref. 2), a bias such as a spring is used. It is known to have a configuration in which the ball is moved using the means iii). That is, when conveying a fluid with high viscosity, frictional resistance acts on the ball etc. which are plate bodies, and seating of a ball etc. becomes slow, and the fluid flows back inside a flow path in the meantime. As a result, the discharge flow rate in the pump decreases, affecting the pump quantitative property and the like. Therefore, according to the prior art, as described above, in order to accelerate the seating of the ball, which is a plate body, a urging means such as a spring is provided on the upper part of the ball.

However, in the reciprocating pump disclosed in Reference 1, a relief plate 27 for controlling the flow of hydraulic oil and an exhaust plate 18 for discharging gas, such as air mixed or generated in the hydraulic oil, are essential. There was a problem that the gas discharge work using this gas discharge part was complicated.

In the reciprocating pump according to the prior art, since the diaphragm is reciprocated with the working oil, there may be a case where gas such as air is mixed into the working oil when the pump is assembled or when the pump is driven. In the reciprocating pump configured to reciprocate the diaphragm with the working oil, it is preferable to avoid such gas mixing. Therefore, in the reciprocating pump according to the prior art, a configuration (gas discharge section) for discharging gas is provided between the diaphragm and the plate unit, and at the time of initial operation after assembling the reciprocating pump, and at the time of gas mixing during continuous operation. It is comprised so that enemy gas discharge may be performed.

Gas discharge | emission performed using the said mechanism is performed by removing a cover part, such as a bolt provided on the gas discharge part, and making a suction port etc. communicate with this gas discharge part. In addition, when discharging this gas, the oil discharge may flow along with the gas in the gas discharge part, so an oil pan or the like must be prepared around the gas discharge part.

In addition, even in the case where the plate unit is installed in the vicinity of the plate unit or in the relief plate, the gas mixed with the hydraulic oil may be removed, but in the prior art of Reference 1, since the structure of the relief plate is unclear, the hydraulic oil adjustment and the gas The relationship with emissions is not clearly recognizable.

That is, in the prior art, a gas gas discharge unit for discharging gas or a relief plate capable of discharging gas is provided, but the former requires complicated work for discharging gas, and the latter has a structure. There is a problem that the result and the like cannot be grasped clearly because it is not clear and actively discharges gas.

Further, in the non-return plate according to the prior art of Reference 2, the ball of the plate body is moved using a biasing means such as a spring in order to reliably block the flow path, but in such a configuration, There was a fear that the resistance between the plate and the seat was increased, the capacitation and the like occurred during the suction process, and the pump capacity was lowered. In addition, when a strong spring or the like is used, it is necessary to perform a "priming liquid" because the fluid is not self-contained at the time of starting the pump. In addition, since the ball is pressed against the seat by a spring or the like when the flow path is closed, there is a problem that the ball, the seat and the like are worn locally or unevenly.

In addition, in the case of using the reciprocating pump according to the prior art, when conveying a high viscosity fluid (adhesive liquid), there was a problem in that the fluid could not be quantitatively adequately conveyed even when the backflow preventing plate or the like was used. . Specifically, when the viscosity of the fluid is high, it is difficult for the fluid to flow, and simply driving a reciprocating means such as a diaphragm does not adequately inhale the fluid, thus making it difficult to realize quantitative conveyance.

Then, an object of this invention is to provide the reciprocating pump provided with the gas discharge mechanism which can discharge gas suitably and automatically, without performing complicated work etc ..

Another object of the present invention is to provide a seat which can reliably block the flow path, and which can reduce local or non-uniform wear of a ball or a seat without using a priming liquid or the like.

Furthermore, an object of the present invention is to provide a reciprocating pump capable of realizing a quantitative conveyance even when conveying a fluid of high viscosity.

According to the present invention, there is provided a diaphragm reciprocating to convey a fluid, a diaphragm driving chamber provided with the diaphragm, and a driving force supply unit for supplying a driving force for reciprocating the diaphragm, wherein the driving force of the driving force supply unit is interposed with hydraulic oil. It is configured to be transmitted to the diaphragm in the diaphragm driving chamber, Between the driving force supply unit and the diaphragm driving chamber is provided with a hydraulic oil limiting chamber for limiting the hydraulic oil, the first gas discharge unit installed in an upper position in the hydraulic oil limiting chamber And a second gas discharge portion provided at an upper position in the diaphragm drive chamber, wherein the first gas discharge portion and the second gas discharge portion communicate with each other to form one gas discharge mechanism. The second gas from the first gas outlet; The reciprocating pump is provided for conveying the fluid backflow prevention body is provided to prevent reverse flow of the fluid portion of the gas emission.

According to such a structure, since several gas discharge parts (1st and 2nd gas discharge part) are communicated and one gas discharge mechanism is comprised, the gas discharged from several gas discharge part is discharged by one gas discharge part. It can be discharged properly just by adjusting the mechanism.

In addition, the hydraulic fluid limiting chamber is provided with a plate that is connected to the diaphragm and driven together with the diaphragm, and a seat that is fitted with the plate to limit the hydraulic oil supplied to the diaphragm drive chamber. One end portion of the first gas discharge portion is provided between the driving force supply portion and the seat in the restriction chamber, and one end portion of the second gas discharge portion is provided between the seat and the diaphragm in the diaphragm chamber. It is preferable that the configuration is made.

According to this preferred configuration, by using the plate or the like, an overload or the like on the diaphragm is appropriately restricted, and the first gas discharge unit and the second and the second gas discharge unit and the second and second seats (diaphragm drive chamber and operating oil restriction chamber) are respectively restricted. Since the gas discharge portion is provided, it is possible to properly discharge the gas around the diaphragm.

Moreover, when the other end part of the said 1st gas discharge part and the other end part of the said 2nd gas discharge part are provided in close proximity, when a fluid is discharged from the said 1st gas discharge part, it is based on the said pressure of the said 2nd gas discharge part. Pressed by the other end of the second gas outlet to close the other end of the gas outlet, and when the fluid is discharged from the second gas outlet, open the other end of the second gas outlet by the pressure of the fluid. The reverse flow prevention body is preferably provided on the other end of the second gas discharge part so as to be lifted from the other end of the second gas discharge part.

According to this preferred configuration, the reverse flow prevention member is provided as a configuration in which two gas discharge portions communicate with each other, so that backflow of the gas and the hydraulic oil to the diaphragm drive chamber side can be prevented and the reciprocating pump can be properly driven.

In addition, the gas discharge mechanism is configured to include the first gas discharge portion, the second gas discharge portion, the backflow preventing body, and the fluid discharge adjusting portion, wherein the fluid discharge adjusting portion is provided on the upper portion of the backflow preventing body. The structure comprised including a ball body and the adjustment valve which can adjust the lift amount of the said ball body is preferable.

According to this preferred configuration, it is preferable that the gas is automatically discharged from the first gas discharge portion and the second gas discharge portion with the lift amount and the lift amount of the ball body at predetermined intervals, respectively.

In this case, it is preferable that the lift amount of the backflow preventer is about 0.5 mm to 2.0 mm, and the lift amount of the ball body is about 0.5 mm to 2.0 mm. The lift amount of the backflow preventer is more preferably about 1.0 mm to 1.5 mm, and more preferably about 0.5 mm to 1.0 mm as the lift amount of the ball body.

Moreover, it is preferable that the said backflow prevention body is a ball body, and is comprised using the material which has a specific gravity close to the specific gravity of automatic oil. Examples of the material having a specific gravity close to the specific gravity of the hydraulic oil include polypropylene and the like.

In addition, a configuration in which a hydraulic oil replenishment mechanism is provided to refill hydraulic oil discharged from at least one of the first gas discharge portion and the second gas discharge portion is preferable.

As the hydraulic oil replenishment mechanism, for example, an auxiliary plunger mechanism configured to presuppose the outflow of the hydraulic oil at the time of gas discharge and supply the corresponding hydraulic oil, or a hydraulic oil supply plate capable of supplying an appropriate hydraulic oil in response to pressure fluctuations in the diaphragm drive chamber ( Hydraulic oil supply plate which can change the replenishment pressure).

According to this preferred configuration, since the hydraulic oil replenishment mechanism (auxiliary plunger mechanism, hydraulic oil replenishment plate, etc.) is provided, the hydraulic oil replenishment or diaphragm drive chamber corresponding to the hydraulic oil at the time of gas discharge is considered in advance. It is possible to appropriately supply the hydraulic oil when the excessive negative pressure is reached, and it is possible to maintain the operation of the reciprocating pump in a stable state without reducing the pump efficiency.

According to another feature of the present invention, there is provided a main body portion having a flow path of a fluid, a plate body installed in the main body part to open and close the flow path, and a biasing means provided in the main body part to apply a bias force to the plate body. A backflow prevention plate constructed by use of the back flow prevention means, wherein the urging means is provided on the inlet side of the fluid in the flow path to the plate body, and when the flow path is blocked by the plate body, between the plate body and the urging means. There is provided a non-return plate, characterized in that it has a predetermined interval.

According to such a structure, since the said board body is urged by the urging means to the inlet side of the said fluid, the blockage of the said circulation path in the said fluid can be improved. According to such a configuration, when the distribution path is closed by the plate, the predetermined space is provided between the taxing means and the plate, so that the plate is forced to the plate by the taxing means. It is not pressed. Therefore, according to such a structure, abrasion of the said board body, a seat, etc. can be reduced effectively.

According to another feature of the present invention, there is provided a main body portion having a fluid flow path and a plate body provided in the main body portion to open and close the flow path, and at least outside the main body portion and the main body portion. The electromagnet means is provided in one side, and the said board body is comprised using the magnetic material, and according to the opening / closing timing of the said distribution path | route made with the said board body, one of the energization timing and polarity switching timing with respect to the said electromagnet means is determined. There is provided a non-return plate. Moreover, in the said structure, when the said electromagnet means is provided in the said main-body part, it is not provided in the said distribution path but is installed in the wall part which draws the said distribution path. Or you may comprise so that the said board main body itself may function as an electromagnet means instead of providing the said electromagnet means separately.

According to such a structure, since the said board body moves using the said electromagnet means, the said board body can be moved suitably by adjusting the electricity supply timing etc. with respect to the said electromagnet means. That is, since it is possible to obtain a backflow prevention plate having high responsiveness during operation, the flow path can be opened and closed at an appropriate timing even in the case where the viscosity of the fluid is high.

Moreover, in this structure, since the said plate body is movable by the said electromagnet means, the said plate body can be lifted and the said distribution path can be made open. Therefore, according to this structure, by discharging the said plate | board body by opening the said plate body by the washing | cleaning liquid in a line or the conveying fluid in a line after line washing, discharge, collection | recovery, etc. can be easily carried out as needed.

In addition, a configuration in which a capacitor is installed in the power supply line for the electromagnet means is preferable. According to this configuration, a large power supply can be instantaneously supplied to the electromagnet means, and a large electromagnetic force can be generated in the electromagnet means, whereby a backflow prevention plate having a higher closing response can be obtained.

In addition, according to another feature of the present invention, a reciprocating motion of a first diaphragm and a second diaphragm reciprocating to convey fluid, a diaphragm drive chamber provided with the first and second diaphragms, and the first and second diaphragms A driving force supply unit for supplying a driving force for driving the driving force supply unit, wherein the driving force supply unit includes one eccentric cam, a first piston and a second piston unit reciprocating by rotation of the eccentric cam, The driving force of the first and second piston portions is configured to be transmitted to the first and second diaphragms via the hydraulic fluid, and to convey the fluid having an auxiliary drive portion installed to convey the fluid to the fluid transfer chamber in the diaphragm drive chamber. A reciprocating pump is provided.

A first auxiliary diaphragm and a second auxiliary diaphragm reciprocating to convey the fluid, and an auxiliary eccentric cam reciprocating the first and second auxiliary diaphragms, wherein the auxiliary eccentric cam drives the eccentric cam It is preferable to use a driving force transmission shaft to make a rotation drive. The auxiliary eccentric cam may be configured to rotate in the same cycle using the driving force transmission shaft.

Furthermore, according to another feature of the present invention, there is provided a diaphragm for reciprocating to convey fluid, a diaphragm drive chamber provided with the diaphragm, and a driving force supply for supplying a driving force for reciprocating the diaphragm, the upstream side of the diaphragm And a reverse flow prevention plate respectively provided on the downstream side, the reverse flow prevention plate having a flow path of the fluid, a plate body installed in the main body part to open and close the flow path, and a force applied to the plate body. A reciprocating pump for conveying a fluid having a predetermined interval between the plate body and the urging means when the plate body is urged on the inlet side of the fluid in the flow path, and when the flow path is blocked by the plate body. Is provided.

According to another feature of the present invention, there is provided a reciprocating motion between a first diaphragm and a second diaphragm reciprocating to convey a fluid, a diaphragm drive chamber provided with the first and second diaphragms, and the first and second diaphragms. A driving force supply unit for supplying a driving force for driving the driving force supply unit, the driving force supply unit including one eccentric cam, a first piston unit and a second piston unit reciprocating by rotation of the eccentric cam, The driving force of the second piston unit is configured to be transmitted to the first and second diaphragms via the hydraulic fluid, and an auxiliary drive unit is provided to convey the fluid to the fluid transfer chamber in the diaphragm drive chamber, and the auxiliary drive unit supplies the fluid. A first auxiliary diaphragm and a second auxiliary diaphragm reciprocating to be conveyed, and the first and second beams With auxiliary eccentric cam for reciprocating the diaphragm, the auxiliary eccentric cam, with the driving force transmitting shaft for driving the eccentric cam is driven to rotate. The auxiliary eccentric cam may be configured to be rotationally driven at the same period using a driving force transmission shaft for driving the eccentric cam. In addition, a backflow prevention plate is provided on the upstream side and the downstream side of the first and second diaphragms, respectively, and the backflow prevention plate is provided in the main body portion having a flow path of the fluid and in the main body part to open and close the flow path. And a biasing means provided in the main body so as to exert a biasing force on the plate, and the biasing means is provided to bias the plate on the inlet side of the fluid in the flow path. When the flow path is closed by the plate, a reciprocating pump for conveying a fluid having a predetermined interval between the plate and the urging means is provided.

Furthermore, according to another feature of the present invention, there is provided a diaphragm for reciprocating to convey fluid, a diaphragm drive chamber provided with the diaphragm, and a driving force supply for providing a driving force for reciprocating the diaphragm, the upstream side of the diaphragm And a reverse flow prevention plate respectively provided on the downstream side, wherein the reverse flow prevention plate is configured using a main body portion having a flow path of a fluid, and a plate body provided in the main body part to open and close the flow path, and at least the main body part and Electromagnet means is provided at one outside of the main body, and the plate is made of a magnetic material, and the energization timing and the polarity switching timing of the electromagnet means are in accordance with the opening and closing timing of the flow path performed by the plate. Reciprocating motion for conveying fluid in which either side is determined A pump is provided. In addition, in the said structure, when the said electromagnet means is provided in the said main-body part, it is not provided in the said distribution path but is installed in the wall part which draws the said distribution path. Or you may comprise so that the said board main-body part itself may function as an electromagnet means instead of providing the said electromagnet means separately.

According to another feature of the present invention, there is provided a first diaphragm and a second diaphragm reciprocating to convey a fluid, a diaphragm drive chamber provided with the first and second diaphragms, and a driving force for reciprocating the diaphragm. And a driving force supply unit comprising a single eccentric cam, a first piston unit and a second piston unit reciprocating by rotation of the eccentric cam, and driving force of the first and second piston units. It is configured to be delivered to the first and second diaphragm via the hydraulic fluid, and an auxiliary drive unit is provided to convey the fluid to the fluid transfer chamber in the diaphragm drive chamber, and the auxiliary drive unit is configured to reciprocate to convey the fluid. A first auxiliary diaphragm and a second diaphragm, and the first and second auxiliary diaphragms It has an auxiliary eccentric cam which double-moves, The said auxiliary eccentric cam is driven to rotate using the drive force transmission shaft which drives the said eccentric cam, A backflow prevention plate is provided in the upstream and downstream of the said 1st and 2nd diaphragm, respectively. And the backflow prevention plate is configured using a main body portion having a flow path of the fluid and a plate body provided in the main body part to open and close the flow path, and at least one of the main body part and the outside of the main body part. Is provided, and the said board body is comprised using the magnetic material, and conveys the fluid in which one of the electricity supply timing and the polarity switching timing with respect to the said electromagnet means is determined according to the opening-closing timing of the said distribution path | route made with the said board body. A reciprocating pump for the purpose is provided. In addition, in the said structure, when the said electromagnet means is provided in the said main-body part, it is not provided in the said distribution path but is provided in the wall part which draws the said distribution path. Or you may comprise so that the said board main body itself may function as an electromagnet means instead of providing the said electromagnet means separately.

It is preferable that a capacitor is installed in the power supply line for the electromagnet means. According to such a structure, it becomes possible to obtain the reciprocating pump which has a backflow prevention plate with high closing responsiveness, etc., and can implement high-precision fixed quantity conveyance.

According to another feature of the invention, in the reciprocating pump including the first and second diaphragms reciprocating in contact with the fluid to be conveyed, the contact surface of the first diaphragm and the contact surface of the second diaphragm are And the pumping head has a conveying path so as to be substantially parallel to each other, and a fluid conveying area is formed using the contacting surface of the first diaphragm, the contacting surface of the second diaphragm, and the pump head. A reciprocating pump is provided.

Here, the "fluid conveying area" means that each diaphragm (first diaphragm, second diaphragm) is driven to leak the pipe section connected to the conveying path of the pump head (the path where the fluid installed in the pump head is conveyed). It is the area | region which can convey the said fluid appropriately without work.

According to such a structure, since two diaphragms face each other and are installed via the pump head, compared with a pump having only two independent pump head parts, the number of parts in constructing a reciprocating pump is greatly increased. Can be reduced. In addition, since the number of sealing parts can be reduced with a decrease in the number of parts, the likelihood of the liquid leaking by the decrease of the sealing part can be reduced. In addition, since it is possible to reduce the number of parts, the probability of occurrence of manufacturing error and assembly error of each component can be reduced. According to such a configuration, since the pump head is provided between the diaphragms facing each other, each diaphragm can appropriately move a predetermined movement without causing the movement of the first diaphragm to adversely affect the second diaphragm or vice versa. Can be done. Therefore, according to the reciprocating pump of such a structure, the discharge flow volume in each diaphragm can be hold | maintained suitably, and the pulsation of a conveying fluid can be prevented effectively.

In addition, in the reciprocating pump according to the present invention, a configuration in which a conveying fluid distribution block including the diaphragm and the pump head is detachable without leaking the fluid from the fluid conveying region is preferable. According to this separable structure, it becomes possible to perform maintenance processing efficiently. That is, according to such a reciprocating pump, it is possible to take out a piping part etc. without disassembling a conveying fluid distribution block, and to carry out maintenance of a drive force supply part (for example, exchange of an eccentric cam, a positional regulating means, etc.). Therefore, as in the conventional pump having two independent pump head parts, maintenance processing can be performed without disassembling or assembling two pump head parts. Therefore, the reciprocating pump excellent in maintenance property which can carry out maintenance of the said drive force supply part etc. without removing the conveying fluid which distribute | circulates in the said conveying fluid distribution block beforehand can be obtained.

According to another aspect of the present invention, a reciprocating pump including a diaphragm reciprocating in contact with a fluid to be conveyed, and a driving force supply unit for driving the diaphragm, wherein the driving force supply unit includes one eccentric cam and the eccentricity. A first piston portion and a second piston portion reciprocating by the rotation of the cam, and adjustment means for adjusting the positions of the first and second piston portions, wherein the adjustment means is the first piston portion. And a function of biasing the biasing force in a direction in which the eccentric cam is located, and a second piston part generated between the first piston part and the second piston part due to a change in the diagonal distance of the eccentric cam. There is provided a reciprocating pump having a damping function to absorb gaps.

According to such a structure, since it is comprised so that two piston parts may be driven by one eccentric cam, the identity of an eccentric cam shape etc. is not required compared with the case of using two eccentric cams. Therefore, it is possible to efficiently manufacture and assemble the reciprocating pump and each component without requiring high assembly precision or the like as in the case of using two eccentric cams.

Moreover, the said 2nd piston part is formed in the empty state, the said eccentric cam and the said 1st piston part are provided in the inside of the said 2nd piston part, and the outer surface part of the said 1st piston part, and the said 2nd It is preferable that the said adjustment means is provided between the inner surface parts of a piston part, and that the said 1st piston part and the said 2nd piston part reciprocate with the said adjustment means by rotation of the said eccentric cam.

According to this preferred configuration, the reciprocating motion is repeated while the piston parts slide while the adjustment means (position regulating biasing means) are inserted by the rotation of the eccentric cam. The maximum bending distance of the adjusting means can be made quite small. Therefore, according to this preferred configuration, since the adjustment means can be configured by using a compact and low-strength urging means (spring or the like), further miniaturization of the reciprocating pump can be realized.

In addition, in the reciprocating pump according to the present invention, a configuration in which the reciprocating directions of the first and second piston portions, the biasing direction and the buffering direction of the adjusting means are substantially parallel is preferable.

In addition, in the reciprocating pump according to the present invention, it is preferable that the adjusting means is configured using a biasing member made of one spring or the like.

Furthermore, in the reciprocating pump according to the present invention, a first space formed between the cross section of the first piston portion and one diaphragm, and a second space formed between the cross section of the second piston portion and another diaphragm Each of these spaces is configured in a substantially closed state, and each of the spaces is filled with hydraulic oil, and a pressure acts on the hydraulic oil based on the reciprocating motions of the first and second piston portions, thereby causing the pressures of the 1 and It is preferable that another diaphragm reciprocates.

According to this preferred configuration, it is possible to effectively transmit the driving force from the piston to the diaphragm, and a reciprocating pump capable of miniaturization and the like can be obtained by using the driving force supply unit having various effects described above.

According to another aspect of the present invention, there is provided a reciprocating pump including a diaphragm reciprocating in contact with a fluid to be conveyed, and a driving force supply unit for driving the diaphragm, wherein the driving force supply unit includes one eccentric cam, and A first piston portion and a second piston portion reciprocating by rotation of the eccentric cam, and a contact transmission element (rotating shaft) in contact with the eccentric cam so as to transmit the driving force of the eccentric cam to the respective piston portions, The contact transmission element (rotation shaft) is formed to have a smaller diameter than the eccentric cam so as to suppress the pressure angle generated between the eccentric cam and the contact transmission element (rotation shaft). That is, in the reciprocating pump according to the present invention, it is preferable that the contact transmission element (rotation shaft) is formed as small as possible.

According to such a structure, by forming the said contact transmission element (rotation shaft) as small as possible, the pressure angle which generate | occur | produces with the said eccentric cam is made small, and the life of a reciprocating pump is extended, and the long term Pulseless conveyance can be realized.

Furthermore, in the reciprocating pump according to the present invention, bearings are provided in the respective piston parts, each bearing further comprising an inner ring unit having a plurality of rings for supporting the corresponding contact transmission element (rotating shaft). It is preferable to have. According to this preferred configuration, since the contact transmission element (rotation shaft) is in contact with the eccentric cam and the inner ring side of the ring, the eccentric cam is in contact with the contact transmission element (rotation shaft) along the outer ring side of the bearing. In comparison, the pressure angle between the eccentric cam and the contact transmission element (rotary shaft) can be made smaller. By doing so, the life of a reciprocating pump can be extended as mentioned above.

Furthermore, in the reciprocating pump according to the present invention, two or more bearings are provided in each of the piston parts, and in each of the piston parts, the contact transmission element (rotating shaft) is supported by the bearing and the eccentric cam. The configuration in which is installed is preferable. According to this preferred configuration, if the contact transmission element (rotation shaft) has a predetermined strength or the like, the contact transmission element can be made to the minimum size necessary without being influenced by the size of the bearing or the eccentric cam. Therefore, the pressure angle can be made small as mentioned above, and the life of a reciprocating pump can be extended.

Furthermore, in the reciprocating pump according to the present invention, an adjusting means for adjusting the position of the first piston portion and the second piston portion is provided, and the adjusting means is provided with the contact provided in the first and second piston portions. The function of biasing the transmission element in the direction in which the eccentric cam is located, and the gap generated between the first piston portion and the second piston portion due to the change in the diagonal distance of the eccentric cam can be absorbed. It is preferable to have a buffer function. The adjustment means includes, for example, a biasing means such as a spring.

According to another feature of the present invention, there is provided a reciprocating pump including a diaphragm reciprocating in contact with a fluid to be conveyed, and a driving force supply unit for driving the diaphragm, wherein the driving force supply unit includes one eccentric cam and the eccentricity. A first piston portion and a second piston portion reciprocating by the rotation of the cam, and a contact transmission element (rotating shaft) in contact with the eccentric cam so as to transmit the driving force of the eccentric cam to each of the piston portions. There is provided a reciprocating pump provided with a drive storage mechanism capable of adjusting the drive state of the diaphragm.

According to such a configuration, since the driving state of the diaphragm can be adjusted appropriately by providing the drive adjusting mechanism, the diaphragm is corrected so as to compensate for the decrease in the pulsating portion even when pulsation or the like is issued to the discharge side of the reciprocating pump. It becomes possible to drive and the reciprocating pump which can prevent pulsation effectively can be obtained.

Furthermore, in the reciprocating pump according to the present invention, the driving force of the piston portion is configured to be transmitted to the diaphragm via the hydraulic oil, and the drive adjustment mechanism includes the auxiliary plunger and the auxiliary plunger which are driven in accordance with the movement of each piston portion. It is preferable to have an adjustment plunger capable of adjusting the working time, and the auxiliary plunger presses the hydraulic oil so that the driving state of the diaphragm is adjusted.

According to this preferred configuration, even if pulsation or the like occurs on the discharge side of the reciprocating pump, the diaphragm can be driven to pressurize the hydraulic oil by the auxiliary plunger to correct the pulsation portion. Thus, a reciprocating pump capable of effectively preventing pulsation can be obtained.

Furthermore, in the reciprocating pump according to the present invention, it is preferable that the adjustment plunger is configured such that the interval between the auxiliary plunger and the adjustment plunger regulates the working time of the auxiliary plunger, and the interval can be arbitrarily set. . According to this preferred configuration, since the operating time of the auxiliary plunger can be arbitrarily set, even if various pulsations or the like occur due to the difference in the model of the pump, the adjustment using the adjustment plunger can be performed for each pump. It is possible to obtain a reciprocating pump capable of effectively preventing pulsation.

Further, in the reciprocating pump according to the present invention, the drive adjustment mechanism drives the variable speed motor for driving the eccentric cam, a rotation position detector capable of detecting the position of the eccentric cam, and the eccentricity detected by the rotation position detector. It is preferable that a control means capable of controlling the variable speed motor on the basis of a signal indicating the position of the cam is configured.

According to this preferred configuration, since the variable speed motor can be controlled by using the position signal and the control means, the rotational speed of the eccentric cam for driving the diaphragm can be appropriately controlled. Therefore, even if pulsation or the like has occurred, a reciprocating pump capable of effectively preventing pulsation or the like can be obtained by controlling the rotation of the eccentric cam and controlling the driving state of the diaphragm as necessary.

Furthermore, in the reciprocating pump according to the present invention, a pulsation detecting means is provided on the discharge side of the fluid conveying path, and the pulsation signal detected by the pulsation detecting means is fed back to the control means, and the position signal and Preferably, the variable speed motor is controlled based on the pulsation signal and the control means. Here, as the pulsation detecting means, it is preferable to use detecting means such as a flow meter or a pressure gauge capable of detecting any form of pulsation of the conveying fluid.

Furthermore, in the reciprocating pump according to the present invention, it is preferable that the variable speed motor is a stepping motor. Moreover, the structure whose rotation position detector is a rotary encoder or a taco generator is preferable.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described based on drawing.

1 shows a schematic cross-sectional view of a reciprocating pump according to an embodiment of the present invention. As shown in FIG. 1, the reciprocating pump which concerns on this embodiment implements the fluid conveyance part 10A which conveys a fluid by reciprocating a diaphragm (1st diaphragm 1A and 2nd diaphragm 1B). , 10B, a driving force supply unit 40 for supplying hydraulic oil at an appropriate timing to drive these diaphragms 1A, 1B, and a driving unit 70 for driving the eccentric cam 42 of the driving force supply unit 40. It is comprised including these.

Moreover, the drive part 70 which comprises this reciprocating pump has the electric motor 71 which generate | occur | produces a rotational motion, and the gear part 72 for transmitting the rotational force from this electric motor 71 to the drive force transmission shaft 41. FIG. ) And the like. In addition, in the reciprocating pump according to the present embodiment, the auxiliary plunger mechanisms 100A and 100B (corresponding to the `` working oil replenishment mechanism '' of the present invention) and the hydraulic oil supply plates 150A and 150B are respectively provided on the left and right sides of the driving force supply part 40. Corresponding to the "working oil replenishment mechanism" of the invention) is provided. These will be described later in detail.

In addition, the reciprocating pump according to the present embodiment includes two fluid conveying units 10A and 10B in order to prevent pulsation, but they are basically the same in configuration only with different driving timings. In addition, in this embodiment, it has two fluid conveyance parts 10A and 10B, and in this embodiment, the other element (for example, the auxiliary plunger mechanism 100A, 100B mentioned above and hydraulic fluid supply plate 150A, 150B etc.) Also, two of the same structure are provided corresponding to the fluid conveyance parts 10A and 10B, respectively.

Therefore, hereinafter, the same components will be used to describe the same components, and when distinguishing from each other, the symbols "A" and "B" will be appended as necessary.

FIG. 2 is a sectional view taken along the line II-II of FIG. 1, and specifically, a sectional view of the driving force supply part 40. In addition, description of the auxiliary plunger is abbreviate | omitted in this FIG.

As shown in FIG. 2, the driving force supply unit 40 includes a driving force transmission shaft 41 that receives the driving force from the driving unit 70 described above, an eccentric cam 42 attached to the driving force transmission shaft 41, and Inner ring of the piston portion (the first piston portion 43 and the second piston portion 44) reciprocating in accordance with the movement of the eccentric cam 42 and the bearing 47 in the first piston portion 43. The first pivot shaft 45 supported by the unit, the second pivot shaft 46 supported by the inner ring unit of the bearing 48 in the second piston portion 44, and the second piston portion 44. ), The first piston portion 43 and the second piston portion 44 are properly applied, and the respective rotation shafts 45 and 46 provided in the respective piston portions 43 and 44 are eccentric cams ( And a position regulating bias means 49, which is an adjusting means which functions to be brought into contact with 42), and a casing portion 50 containing each of these elements. In the driving force supply part 40 having the above elements, the hydraulic oil is filled in the sealed space between the inner wall of the casing part 50 and the piston parts 43 and 44.

In the driving force supply part 40 which concerns on this embodiment, the 2nd piston part 44 is formed in the empty state. That is, the second piston portion 44 has a drive force transmission shaft 41, an eccentric cam 42, a first piston portion 43, a bearing 48, and a positional regulating means 49 therein. It is comprised so that these may be included. And between the inner wall part (inner surface part) 44a of the 2nd piston part 44 and the outer wall part (outer surface part) 43a of the 1st piston part 43, the position regulating biasing means 49 is inserted, have. That is, by this position regulating bias means 49, the force is applied to the first and second piston parts 43 and 44 in the direction in which the eccentric cam 42 is located. In other words, the first rotational shaft 45 in the first piston portion 43 and the second rotational shaft in the second piston portion 44 are generated by the appropriate biasing force of the position regulating biasing means 49. The 45 is always urged to contact the outer circumferential surface of the eccentric cam 42.

Moreover, the casing part 50 is provided with the supply port of hydraulic fluid (the 1st supply port 51 and the 2nd supply port 52) so that it may communicate with each piping part (to be mentioned later). And the space formed between the diaphragm 1, 2 through the supply port 51, 52, piping part 21, 22, etc. from the edge surface part of each piston part 43, 44 is almost sealed. It consists of a state, and hydraulic fluid is filled in this space. Therefore, in the present embodiment, the positive pressure and the negative pressure act on the hydraulic fluid as the piston portions 43 and 44 move, and the hydraulic fluid flows through the supply ports 51 and 52 by this pressure fluctuation. Done. The hydraulic fluid causes the diaphragms 1 and 2 to reciprocate.

3 is a partial enlarged view of the reciprocating pump shown in FIG. 1, and specifically, an enlarged view of the fluid conveyance unit 10. In addition, although the reciprocating pump which concerns on this embodiment is comprised including two fluid conveyance parts 10A and 10B as mentioned above, the structure is basically the same. Therefore, in this FIG. 3, description of "A" and "B" for distinguishing between right and left is abbreviate | omitted. When the left and right distinction is required in the description, the components on the left side of the drawing are denoted by "A", and the components on the right side are denoted by "B".

As shown in FIG. 3, in this embodiment, each diaphragm 1A, 1B is fitted using the pump head 32 and the hydraulic oil supply part 31A, 31B of right and left, and each fluid conveyance part 10A, 10B. ) Is configured. Specifically, the fluid conveying part 10 includes a diaphragm 1, a pump head 32, a hydraulic oil supply part 31 for supporting the diaphragm 1 together with the pump head 32, and the hydraulic oil supply part 31. It is configured to include a gas discharge mechanism 20 and the like installed on the top.

 And using this hydraulic oil supply part 31 and the pump head 32, the diaphragm drive chamber 2 provided with the diaphragm 1 is comprised, The board body connected to the diaphragm 1 in the hydraulic oil supply part 31 is comprised. (3) and the hydraulic oil restriction chamber 5 provided with the board | substrate 4 corresponding to this is comprised. In addition, the gas discharge mechanism 20 mentioned above is provided in order to discharge | emit appropriately the gas (air etc.) mixed in the hydraulic oil in the diaphragm drive chamber 2 and the hydraulic oil restriction chamber 5. In addition, the pump head 32 is provided with an inflow side backflow prevention plate 33 that functions to inject the conveying fluid and an outflow side backflow prevention plate 34 that functions to outflow the conveying fluid, respectively. It communicates with the fluid conveyance chamber 2a of the diaphragm drive chamber 2 via the inflow path 33a and the outflow path 34a.

In the diaphragm drive chamber 2, the diaphragm 1 receives the drive force from the drive part 70 mentioned above via the drive force supply part 40, and is comprised so that the diaphragm 1 may reciprocate based on this drive force. Specifically, the driving force supply part 40 and the hydraulic oil supply part 31 communicate with each other via the hydraulic oil piping part 35, and the hydraulic oil piping part 35 and the hydraulic oil supply part 31 are filled with hydraulic oil, and the driving force supply part ( The reciprocating motion of the piston parts 43 and 44 in 40 is transmitted to the diaphragm 1 via the hydraulic oil in the hydraulic oil piping part 35 and the hydraulic oil supply part 31. As shown in FIG. In addition, although the cross-sectional shape of the diaphragm 1 is formed in the wave shape here, this invention is not limited to this structure, It is possible to make various forms as needed.

In the hydraulic oil restriction chamber 5, as described above, the plate body 3 and the plate seat 4 corresponding thereto are provided, and the plate body 3 is urged such as a coil spring to the plate body support part 6. The plate body 3 is attached via the means 7, and the plate 3 is fixed to the shaft 8 connecting the hydraulic oil limiting chamber 5 and the diaphragm driving chamber 2. Since one side end 8a of the shaft 8 is urged on the diaphragm 1 side via the urging means 7 and the plate body 3, the hydraulic oil supply part 31 of the diaphragm 1 in normal operation. Abuts on the side.

In addition, the hydraulic oil restriction chamber 5 restricts the hydraulic oil supplied to the diaphragm 1, and is installed in order to prevent the diaphragm 1 from reciprocating excessively beyond a predetermined range in detail below.

In addition, the following description is made about the component member of one side among the fluid conveyance parts 10A and 10B, Therefore, description is made only about one side of the two component members provided for each function. Therefore, unless otherwise indicated, the same description shall be applied to the other fluid conveying section.

The shaft support part 9 is provided between the hydraulic oil restriction chamber 5 and the diaphragm drive chamber 2, and the shaft support part 9 is provided with the through-hole 9a for circulating hydraulic fluid. Moreover, the through-hole 6a for circulating hydraulic fluid is formed also in the board | substrate support part 6. As shown in FIG.

In this embodiment, as shown in FIG. 3 etc., since the diaphragm drive chamber 2 and the hydraulic oil restriction chamber 5 are formed, when the gas, such as air, is mixed in hydraulic fluid, each chamber 2, (5) Gas is likely to accumulate at the top of the. Therefore, in this embodiment, the gas discharge mechanism 20 is provided in order to discharge | emit gas in the diaphragm drive chamber 2 and the hydraulic oil restriction chamber 5 suitably. Hereinafter, the structure of the gas discharge mechanism 20 is demonstrated using FIG.

4 shows an enlarged view of the gas discharge mechanism according to the present embodiment. As shown in FIG. 4, the gas discharge mechanism 20 which concerns on this embodiment is installed in the hydraulic fluid restriction chamber 5 by the 1st gas discharge path 21 (corresponding to the "1st gas discharge part" of this invention). Then, the second gas discharge path 22 (corresponding to the "second gas discharge part" of the present invention) provided in the diaphragm drive chamber 2 is provided.

More specifically, the one end 21a of the 1st gas discharge path 21 is provided in the upper position on the hydraulic oil piping part 35 side rather than the seat 4 in the hydraulic oil restriction chamber 5 (FIG. 3), one end 22a of the second gas discharge path 22 is provided at an upper position between the diaphragm 1 and the seat 4 in the diaphragm drive chamber 2 (see FIG. 3). . The other end portions 21b and 22b of the respective discharge paths 21 and 22 are provided in close proximity so as to communicate with the communication portion 24 formed by the fluid discharge adjustment portion 25 and the hydraulic oil supply portion 31. . In addition, a first ball body 23 (corresponding to the "backflow prevention body" of the present invention) is provided on the other end 22b of the second gas discharge path 22, and the first ball body 23 The restricting part 26 which regulates the lift amount (movable area) of the 1 ball body 23 is provided.

The second discharge body 28 provided in the first adjustment part discharge path 25a, which functions to encapsulate or discharge the discharge gas from the communication part 24 by a predetermined amount, is provided in the fluid discharge adjustment part 25 (the " Ball body) and the amount of lift (movable area) of the second ball body 28, and an adjustment function for circulating the discharged gas discharged through the first adjusting unit discharge path 25a. The valve 27 is provided.

The regulating valve 27 has a discharge path 27a in the valve therein. The male screw portion is formed on the outer circumferential portion of the adjustment valve 27 so that the screw can be inserted into the fluid discharge adjusting portion 25, and the lift amount of the second ball body 28 is adjusted by the opening / closing amount of the adjustment valve 27. . Moreover, the in-valve discharge path 27a of the adjustment valve 27 is comprised so that communication with the 2nd adjustment part discharge path 25b formed in the fluid discharge adjustment part 25 is possible. In addition, the second adjusting part discharge path 25b is in communication with the gas discharge pipe part 36 connected to the working fluid accumulation part (in the casing 50) of the driving force supply part 40. In addition, the upper part of the adjustment valve 27 in the fluid discharge adjustment part 25 covers this adjustment valve 27 and the protection cover 29 which can be detached (or opened and closed) at the time of adjustment of the adjustment valve 27. ) Is installed.

The reciprocating pump according to the present embodiment is configured as shown in Figs. 1 to 4 as described above, and functions as follows in normal operation.

In the reciprocating pump according to the present embodiment, first, the electric motor 71 is rotated first, and the rotational force is transmitted to the driving force transmission shaft 41 via the gear portion 72.

Next, the eccentric cam 42 is rotated by the driving force transmission shaft 41, and the first and second piston parts 43 and 44 are reciprocated by the rotation of the eccentric cam 42. Here, the 1st piston part 43 and the 2nd piston part 44 reciprocate integrally with the one eccentric cam 42 based on the structure mentioned above. By the reciprocating motion of the piston parts 43 and 44, pressure of a predetermined force and direction acts on the hydraulic oil, and the hydraulic oil passes through the first and second supply ports 51 and 52 to form a pipe part ( 35A, 35B) will be delivered and discharged.

Next, the diaphragms 1A and 1B reciprocate at an appropriate timing based on the hydraulic oil communicating through the pipe portions 35A and 35B, and the inflow-side backflow prevention plate (1A and 1B) moves by the movement of the diaphragms 1A and 1B. 33) and the outflow side backflow prevention plate 34 are operated to convey the desired liquid.

By the way, in the normal operation, the reciprocating pump according to the present embodiment functions as described above to repeatedly perform the reciprocating motion of the diaphragms 1A and 1B to quantitatively convey the desired fluid. It becomes possible. However, if any problem occurs and excess pressure acts on the diaphragm 1 via the hydraulic oil from the driving force supply part 40 (a large amount of hydraulic oil is stuck in the diaphragm drive chamber 2), the diaphragm 1 is cracked or broken. Etc. may arise. Therefore, in this embodiment, the hydraulic oil restriction chamber 5 is provided. It demonstrates concretely below.

In this embodiment, the plate body 3 also reciprocates together with the diaphragm 1 by the hydraulic oil which flowed into the hydraulic oil supply part 31 via the hydraulic oil piping part 35. Therefore, the diaphragm 1 is not driven only when the hydraulic fluid abnormally flows into the supply part 31 at the time of normal operation, and the plate body 3 also moves to the diaphragm 1 side by excess hydraulic fluid. In the present embodiment, the plate body 3 is configured to contact the seat 4 before problems (cracking, etc.) occur in the diaphragm 1 due to excessive working oil or the like, and the plate body 3 is thus seated. By contacting (4), it is comprised so that supply of hydraulic fluid to the diaphragm drive chamber 2 may be restrict | limited appropriately.

According to the present embodiment, as described above, the plate body 3 is also driven together with the diaphragm 1 in accordance with the supply amount (pressure) of the hydraulic oil, and the plate body 3 and the seat 4 are brought into contact with each other if necessary, so that the shaft support portion Since the hydraulic oil circulated to the diaphragm drive chamber 2 can be interrupted via the through hole 9a of 9), the pressure given to the diaphragm 1 via the hydraulic oil can be appropriately limited.

When the hydraulic oil is properly restricted to the hydraulic oil limiting chamber 5 (the plate 3 and the seat 4 constituting the above), the hydraulic oil in the hydraulic oil limiting chamber 5 loses its place to go, but It is properly flowed into a relief mechanism (not shown) provided between the driving force supply part 40 and the hydraulic oil restriction chamber 5, and this hydraulic oil is returned to the casing 50 which constitutes the driving force supply part 40 and the like.

In addition, when hydraulic fluid is restrict | limited using the board | substrate 3 and the seat 4 in this way, hydraulic fluid will also overflow from the 1st gas discharge path 21 provided in the hydraulic fluid restriction chamber 5. At this time, when the second ball body 28 is pressurized by the adjustment valve 27 to the first adjustment part discharge path without any gap, the hydraulic fluid overflowed to the first gas discharge path 21 is accumulated in the communication part 24. do. In the present embodiment, since the first ball body 23 is provided at the upper end (the other end 22b) of the second gas discharge path 22, the first gas discharge path 21 is thus interposed. Even when the hydraulic oil overflows, the hydraulic oil does not flow back to the second gas discharge path 22.

In addition, when a predetermined gap is provided between the second ball body 28 and the control valve 27, the hydraulic oil overflowed to the first gas discharge path 21 is connected to the communication part 24 and the first adjustment part discharge path ( 25a), the inside of the valve discharge path 27a, the second adjustment part discharge path 25b, and the gas discharge pipe part 36 are returned to the casing 50 or the like. In this case as well, the flow back to the second gas discharge path 22 of the working oil by the first ball body 23 provided at the upper end (the other end 22b) of the second gas discharge path 22 as described above. Is prevented.

In this embodiment, when the diaphragm 1 may be overloaded by some problem, the diaphragm 1 is protected by operating the plate 3 etc. as mentioned above.

Next, in the reciprocating pump according to the present embodiment, when mixed in the diaphragm drive chamber 2 and the hydraulic oil restriction chamber 5 or the like described above, the gas is discharged as follows.

Specifically, in this embodiment, it is comprised so that the gas discharge of the said chambers 2 and 5 can be performed manually or automatically using the gas discharge mechanism 20 which has the fluid discharge | emission adjustment part 25 etc .. FIG.

First, the case where the gas is discharged manually will be described.

When performing manually, as shown in FIG. 4 etc., the 2nd ball body 28 is basically pressed against the upper end part of the 1st adjustment part discharge path 25a using the adjustment valve 27. As shown to FIG. In this state, the gas in the diaphragm drive chamber 20 passes through the second gas discharge path 22, and the gas in the working oil restriction chamber 5 passes through the first gas discharge path 21. It is discharged in, and is stuck here. At this time, the first ball body 23 is provided on the upper portion of the second gas discharge path 22, and a predetermined interval (for example, 1 mm) is provided between the first ball body 23 and the restricting part 26. Since this is provided, the 1st ball body 23 is lifted by the pressure of waste gas, and waste gas is discharged | emitted and accumulated by the communication part 24. FIG.

In the present embodiment, as needed (when the need to discharge gas occurs), the opening and closing amount of the adjustment valve 27 is adjusted (by moving upward), so that the second ball body 28 and the adjustment valve ( 27) to provide a predetermined interval therebetween. When such a space is provided, the second ball body 28 is lifted by the discharge gas pressure in the communication section 24, and the first adjusting part discharge path 25a, the valve discharge path 27a, and the second adjusting part discharge path. The gas in the diaphragm drive chamber 2 and the hydraulic oil restriction chamber 5 is appropriately discharged via 25b and the gas discharge pipe part 36. After the gas discharge is completed, the adjustment valve 27 is twisted again so that the interval between the second ball body 28 and the adjustment valve 27 (the liftable amount of the second ball body 28) is zero.

In this manner, the lift amount of the second ball body 28 (the distance between the adjustment valve 27 and the second ball body 28, that is, the liftable amount of the second ball body 28) is set to "0". Therefore, since the sealed state of the diaphragm drive chamber 2 and the hydraulic oil restriction chamber 5 is maintained in normal operation, gas, hydraulic oil, etc. do not leak outside. Therefore, the reciprocating pump can be operated in a state where the pump performance can be maximized.

In addition, as described above, only one control valve 27 is operated as needed, and two gases can be properly discharged, so that gas discharge (air discharge, etc.) can be performed more easily than conventionally. . In addition, if the gas discharge process (adjustment process of the adjustment valve 27) demonstrated here is basically performed at the time of manufacture of a reciprocating pump, it does not need to be performed so often as much.

Next, the case where gas discharge is performed automatically is demonstrated.

When performing automatically, the space | interval (1st lift amount of the 1st ball body 23) between the 1st ball body 23 and the control part 26 (henceforth a "1st lift amount"). L1 and 2nd ball body The distance between the 28 and the adjustment valve 27 (the side shown by a dotted line (virtual line)) (the liftable amount of the 2nd ball body 28) (henceforth "the 2nd lift amount.") L2 is respectively It is necessary to set at predetermined intervals. Here, the "predetermined interval" means that the gas discharged from each of the gas discharge paths 21 and 22 is appropriately discharged, and the operation is performed in a state in which the pulsation is also suppressed without significantly reducing the discharge effect of the pump. At intervals where possible, this also depends on the discharge amount of the pump and the like. For example, the first lift amount L1 is about 0.5 mm to 2.0 mm (more preferably about 1.0 mm to 1.5 mm), and the second lift amount L2 is about 0.5 mm to 2.0 mm (more preferably 0.5 mm to 1.0 mm). mm) is preferred. In addition, in this embodiment, the restricting part 26 is fixed and the 1st lift amount L1 is set to about 1.0 mm. The second lift amount L2 is set to, for example, about 1.0 mm. However, since this 2nd lift amount L2 is variable by the adjustment valve 27, it is good to adjust it to a more appropriate space | interval (interval in which gas discharge is performed suitably and the pump discharge effect is not reduced so much) as needed. In addition, in order to properly discharge the gas and retain proper sealing properties, it is necessary to appropriately select materials constituting the ball bodies 23 and 28, for example, the first ball body 23 is the specific gravity of the hydraulic oil. It is preferable to configure using a material having a specific gravity close to, for example, preferably using polypropylene or the like.

As described above, in the configuration in which the first lift amount L1 and the second lift amount L2 are determined at predetermined intervals, even if gas is mixed in the diaphragm drive chamber 2 and the operating oil restriction chamber 5 during normal operation, each ball body ( Since the 23 and 28 can be lifted by a predetermined amount, the first gas discharge path 21, the second gas discharge path 22, the communication part 24, the first adjustment part discharge path 25a, and the valve discharge path Gas discharge (air discharge, etc.) can be performed appropriately and automatically via 27a.

As described above, in the present embodiment, when the gas is discharged manually or automatically, not only the gas but also the working oil may be simultaneously discharged. When the hydraulic oil is discharged, the discharge efficiency of the pump may be lowered, and the pulsation may be increased. In the present embodiment, the auxiliary plunger mechanism 100 (see FIG. 1) is provided to replenish the hydraulic oil discharged together with the gas (to prevent a decrease in the pump efficiency when discharging the air). Hereinafter, the plunger mechanism 100 is explained concretely using FIG. 1, FIG. 5, and FIG.

As shown in FIG. 1, in this embodiment, auxiliary plunger mechanism 100A, 100B is provided in the vicinity of the 1st and 2nd piston parts 43 and 44. As shown in FIG. Each auxiliary plunger mechanism 100A, 100B provided on the left and right of the eccentric cam 42 has the same structure fundamentally, respectively. Therefore, below, in FIG. 5 and FIG. 6, it demonstrates using the auxiliary plunger mechanism 100A located in the left side. 5 and 6, the notation of "A" added to the left element is omitted.

As described above, in the reciprocating pump according to the present embodiment, when the gas is discharged, some hydraulic oil is discharged along with the gas. Therefore, the plunger mechanism 100 which concerns on this embodiment is basically replenishing this discharged hydraulic oil, and adjusting the amount of pressurization of hydraulic fluid in order to drive the diaphragm 1 suitably.

5A and 5B show an enlarged view of the auxiliary plunger mechanism that has been configured to perform a predetermined amount of replenishment. Figure 5a shows the start of the start of the auxiliary plunger, Figure 5b shows the end of the drive of the auxiliary plunger. The term " predetermined amount " refers to an amount that enables the reciprocating pump to be operated while realizing a proper pump effect and pulsation state even when the hydraulic oil is discharged along with the gas discharge.

In FIG. 5, the auxiliary plunger mechanism which concerns on this embodiment is comprised including the hydraulic fluid pressure means 110 and the replenishment amount adjustment means 120. As shown in FIG. The hydraulic oil pressing means 110 is a plunger holding part for holding the auxiliary plunger 111 and the auxiliary plunger 111 pressed by the pressing part 115 attached to the first piston part 43 to be able to slide and move. An 112 and a spring holding part 113 fixed to the auxiliary plunger 111, and are provided between the plunger holding part 112 and the spring holding part 113, and the auxiliary plunger 111 is the eccentric cam 42. It is comprised including the spring part 114 attached to the side.

Further, the refill amount adjusting means 120 includes an adjusting plunger 121 for adjusting the working time of the auxiliary plunger 111, an adjusting plunger holding part 122 for holding the adjusting plunger 121 so as to be able to slide and move. And a spring holding part 123 fixed to the adjusting plunger holding part 122, and between the adjusting plunger 121 and the spring holding part 123, the adjusting plunger 121 is connected to the hydraulic oil pressure means 110 side. It is comprised including the spring part 124 attached to the (eccentric cam 42 side).

A male screw portion is formed on the outer circumferential surface of the adjusting plunger holding portion 122, and the male screw portion is formed to fit with the female screw portion formed on the inner circumferential surface of the adjusting means insertion portion 125. That is, in the present embodiment, the refilling amount adjusting means 120 is moved in the arrow X direction (FIG. 5A) by adjusting the position (fitting state) between the adjusting means inserting portion 125 and the adjusting plunger holding portion 122. Reference). Therefore, in this embodiment, the distance t between the edge surface of the auxiliary plunger 111 and the edge surface of the adjustment plunger 121 can be adjusted easily.

In the auxiliary plunger mechanism according to the present embodiment, the edge surface of the auxiliary plunger 111 comes into contact with the edge surface of the adjustment plunger 121 to be a step of replenishing the hydraulic oil. That is, the distance t between the edge surface of the auxiliary plunger 111 and the edge surface of the adjusting plunger 121 defines the replenishment amount of the hydraulic oil. As described above, in the present embodiment, since the distance t (the operating time of the auxiliary plunger 111) can be easily adjusted, the amount of hydraulic oil replenishment can also be easily adjusted.

As described above, Fig. 5A shows the start of driving of the auxiliary plunger 111, and the auxiliary plunger 111 is pressed by the plunger pressing portion 115 in accordance with the movement of the first piston portion 43, Slide in the direction of arrow P (see Figure 5a). When the auxiliary plunger 111 is in contact with the adjusting plunger 121 as shown in FIG. 5B, the auxiliary plunger 111 does not act on the hydraulic oil (no pressure or the like is generated against the hydraulic oil). The state in which the plungers 111 and 121 are in contact with each other indicates the end of driving of the auxiliary plunger 111.

That is, in the reciprocating pump according to the present embodiment, the interval between the plungers 111 and 121 is determined so as to supplement the amount of the hydraulic oil discharged with the gas discharge, thereby increasing the discharge of the hydraulic oil for driving the diaphragm. That is, according to the reciprocating pump according to the present embodiment, the use of the replenishment plunger mechanism 100 makes it possible to replenish the hydraulic oil discharged together with the gas from the gas discharge mechanism 20. The gas can be discharged appropriately manually or automatically without deteriorating the efficiency and causing no pulsation or the like.

In the above-described configuration, if the amount of the hydraulic oil discharged from the gas discharge mechanism 20 is equal to the amount of the hydraulic oil supplied to the auxiliary plunger mechanism 100, the reciprocating pump according to the present embodiment achieves a pump efficiency of 100%. In a configuration in which gas can be secured and the gas is automatically discharged (a configuration having the predetermined first lift amount L1 and the second lift amount L2), even if air is mixed in the operating oil restriction chamber 5 during the pump operation, operation efficiency The air can be discharged out of the pump quickly without degrading it.

In addition, in FIG. 5 and FIG. 6, the case where the auxiliary plunger mechanism 100 replenishes only the quantity of the hydraulic oil discharged | emitted from the gas discharge mechanism 20 was demonstrated, The present invention is not limited to this structure, but is in another part. The setting amount of the auxiliary plunger mechanism 100 may be adjusted so as to cope with the increase and decrease of the hydraulic oil in the same. For example, in the reciprocating pump, a very small amount of liquid may flow back to the inflow side of the liquid in a short time before the chuck ball is seated on the suction side seat. Moreover, the efficiency of hydraulic fluid may fall by the compression of the air which remains in a very small quantity in hydraulic fluid, or the volume change (reduction) of the hydraulic fluid itself under ultra high pressure. Therefore, the auxiliary plunger mechanism may be adjusted so as to refill the amount corresponding to the fluid amount due to the reverse flow and the decrease in the efficiency of the working oil.

6A and 6B show enlarged views of a state in which the flow rate of the auxiliary plunger is adjusted to zero. 6A shows the start of the start of the auxiliary plunger, and FIG. 6B shows the start of the drive of the auxiliary plunger.

As shown in FIG. 6, the adjusted auxiliary plunger 111 and the adjusting plunger 121 are basically connected to the pressing portion 115 attached to the first piston portion 43, similarly to the case described with reference to FIG. 5. Driven by. However, in this FIG. 6, the auxiliary plunger 111 and the adjustment plunger 121 are adjusted so that the press part 115 may contact | connect the auxiliary plunger 111 (refer FIG. 6A). Specifically, by adjusting the fitted state of the adjustment plunger holding portion 122 and the adjustment means inserting portion 125, the refill amount adjusting means 120 is moved in the arrow Y direction (see Fig. 6A) as compared with Fig. 5A. (The replenishment amount adjusting means 120 (adjustment plunger holding part 122) is moved to the position where the auxiliary plunger 111 and the adjustment plunger 121 contact each other).

Therefore, as shown in FIG. 6, the auxiliary plunger 111 and the adjusting plunger 121 are in contact with each other from the start of driving of the auxiliary plunger 111 (see FIG. 6A) to the end of driving (FIG. 6B). Becomes That is, in this adjustment state of FIG. 6, since the distance between the edge surface of the auxiliary plunger 111 and the edge surface of the adjustment plunger 121 is 0, the auxiliary plunger 111 does not have any action on the hydraulic oil.

As shown in FIG. 5 and FIG. 6, the auxiliary plunger mechanism according to the present embodiment can easily adjust the operation time of the auxiliary plunger 111 as necessary. Therefore, according to the present embodiment, it is possible to obtain a reciprocating pump capable of adjusting the replenishment adjustment means 120 appropriately in accordance with the discharge capacity, the pulsation state, etc. for each reciprocating pump, and effectively preventing the pulsation and operating with high discharge efficiency. have.

In addition, in the reciprocating pump according to the present embodiment, as shown in FIG. 1, hydraulic oil supply plates 150A and 150B are provided in the vicinity of the first and second piston parts 43 and 44. The hydraulic oil supply plates 150A and 150B function to supply the hydraulic oil appropriately when the diaphragm drive chamber 2 becomes a negative pressure by the function of the gas discharge mechanism 20 and the like. have. According to this embodiment, since it has these hydraulic oil supply plates 150A and 150B, even if the diaphragm drive chamber 2 etc. become an excessive negative pressure state by any problem, it will start to supply by the hydraulic oil supply plate 150 according to a predetermined pressure. . Therefore, the reciprocating pump according to the present embodiment can maintain a stable function without lowering the pump efficiency.

It is to be noted that the present invention is not limited to the above embodiment, and various changes can be made in addition to those described above without departing from the spirit thereof. For example, in the said embodiment, although the case where the diaphragm was used for the contact part with a conveying fluid was demonstrated, this invention is not limited to this structure, For example, a reciprocating pump is provided by providing a piston or a plunger etc. in a contact part. May be configured.

7 shows the enlarged view of the gas discharge mechanism which comprises the reciprocating pump which concerns on other embodiment. Here, although the embodiment shown in FIG. 7 and the said embodiment demonstrated using FIG. 4 etc. have the same structure fundamentally, the female screw part formed in the fluid discharge adjustment part 25 mainly for installing the adjustment valve 27 is shown. 27) The surroundings are different. Hereinafter, the reason for having such a structure is demonstrated compared with the said embodiment.

In the gas discharge mechanism shown in FIG. 4 and the like, when the air discharge operation is performed at the start of the reciprocating pump, the set pressure of the hydraulic oil supply plate, which is one of the hydraulic oil refilling mechanisms, is set low, and the lift amount of the adjustment valve 27 is set. The pump is driven to the maximum. In this case, the gas in the diaphragm drive chamber 2 and the hydraulic oil restriction chamber 5 is compressed by the drive force of the drive force supply part 40, and is discharged | emitted from the discharge path 27a in a valve. When the gas is discharged to lower the pressure in the diaphragm drive chamber 2 and the hydraulic oil limiting chamber 5, the hydraulic oil is supplied through the hydraulic oil supply plate. At the start of the reciprocating pump, this operation can be repeated to discharge the gas and to fill the hydraulic oil.

However, when the volumetric movement of one rotation of the reciprocating pump is small (when a small diameter piston part or the like is used), a considerable time (for example, several tens of minutes) may be required before the entire gas is discharged. In the gas discharge mechanism shown in FIG. 4 and the like, since the gas can be discharged from the discharge path 27a in the valve only until the second ball body 28 is able to contact the end of the adjustment valve 27 by the gas pressure. When the second ball body 28 comes into contact with the adjustment valve 27 for some reason, the discharge path 27a in the valve may be sealed, and gas may not be properly discharged. Thus, in embodiment shown in FIG. 4, gas discharge may not be appropriately performed in a short time.

Therefore, in order to solve the said problem, in FIG. 7, the female screw part 271 which can attach the adjustment valve 27a is comprised so that it may differ from FIG. That is, according to FIG. 7, the upper part 271a and the lower part 271b of the female screw part 271 are formed in the different size (inner diameter). Specifically, the lower portion of the female screw portion 271b has an inner diameter that is sealed so that no fluid such as gas flows between the adjusting valve 27 and the female screw portion 271 by the O-ring 27c provided in the adjustment valve 27. Formed. Moreover, the upper part of the female screw part 271a is formed with the internal diameter which can release the seal engagement of the O-ring 27c when the lift amount of the adjustment valve 27 is increased.

That is, according to this embodiment shown in FIG. 7, the adjustment valve 27 can be adjusted so that fluid, such as gas, flows between the adjustment valve 27 and the female screw part 271 as needed. Therefore, according to the present embodiment, as shown in FIG. 7 (solid line), even if the second ball body 28 comes into contact with the adjustment valve 27 and the discharge path 27a in the valve is sealed, the gas and the like are It is suitably discharged | emitted from the gas discharge piping part 36 between the adjustment valve 27 and the female screw part 271, and via the bypass discharge path 25c.

In addition, in the configuration as shown in Fig. 7, a piston having a small diameter or the like is used, and in the case of a reciprocating pump having a small discharge capacity (gas discharge capacity), a negative pressure is applied from the outside to the gas discharge pipe 36. Can be forced out of the gas.

In addition, FIG. 8 shows an enlarged view of the gas discharge mechanism forming the reciprocating pump according to another embodiment. Here, although the embodiment shown in FIG. 8 and the said embodiment demonstrated using FIG. 7 etc. have basically the same structure, in this embodiment, the 1st gas discharge path 21 and the 2nd gas discharge path ( The upper bodies 22 are different in that the ball bodies 231 and 232 are provided.

 When the structure as shown in FIG. 8 is used, the specific material of the ball bodies 231 and 232 is not limited to a material close to the specific gravity of the working oil, and a specific ball type having a specific gravity larger than that of a hydraulic oil such as ceramics and close to a perfect spherical shape can be used. Can be. That is, by providing the ball bodies 231 and 232 above the gas discharge paths 21 and 22 in this manner, for example, even when the hydraulic fluid overflows through the first gas discharge path 21, the ball body 232 is provided. ), The working oil does not flow back to the second gas discharge path (22).

The gas discharge mechanism including the ball body such as polypropylene as described above with reference to FIGS. 4 and 7 is applied when constituting a pump of a relatively low pressure, and the gas discharge mechanism including the ball body such as the ceramic described with reference to FIG. The mechanism is applied when constructing a high pressure pump. That is, according to the gas discharge mechanism shown in Fig. 8, the ball bodies 231 and 232 having a relatively large specific gravity such as ceramics are provided above the gas discharge paths 21 and 22, so that the fluid having high viscosity Also, backflow prevention can be appropriately performed.

9A and 9B are schematic cross-sectional views showing the first embodiment of the non-return plate according to the embodiment of the present invention, and specifically, Fig. 9A shows a state where the plate body is seated on the seat and the fluid path is blocked. 9B shows a state in which the plate body is opened from the seat and the fluid path is opened.

As shown in this FIG. 9, the backflow prevention plate which concerns on this embodiment is the upper main-body part 311 and lower main-body part 312 which comprise the plate main-body part 310, and each main-body part 311 and (312). A packing 313 provided between the plate body 314 and the upper guide part 315 and the lower guide part 316 for guiding the plate body 314, the upper main body part 311 and the upper guide part 315. It is comprised including the urging means 317, such as a spring provided in between. In addition, flow passages 311A and 312A for circulating the fluid are formed in the main body portions 311 and 312 constituting the backflow prevention plate.

In the present embodiment, the lower guide portion 316 is fixed to the lower main body portion 312, and the upper guide portion 315 is attached to the upper main body portion 311 via the urging means 317. When the backflow prevention plate is in the closed state (see FIG. 9A), the upper guide part 315 and the lower guide part 316 are in contact with each other (see S part in FIG. 9A). It is comprised so that the predetermined space t1 (refer FIG. 9A) may be provided between plate bodies 314. As shown in FIG.

In the non-return valve configured as described above, when no fluid is supplied, the plate body 314 is seated on the seat 312B of the lower main body 312, and flow paths 311A and 312A are shown in FIG. 9A. Function to block. At this time, since the upper guide portion 315 is configured such that a predetermined interval t1 is provided between the plate body 314 as described above, the plate body 314 does not press the seat 312B tightly.

On the other hand, when fluid is supplied into the backflow prevention plate from the lower main body portion 312 side, as shown in FIG. 9B, the plate body 314 constituting the backflow prevention plate is separated from the plate body 312B in accordance with the pressure of the fluid. At the same time, the upper guide portion 315 is lifted upward in response to the urging force of the urging means 317, and the flow paths 311A and 312A of the fluid in the backflow prevention plate are opened.

After the flow paths 311A and 312A of the non-return plate are opened, and the fluid supply is stopped, the plate body 314 is caused by the self-weight and the biasing force of the taxable means 317 when the fluid supply is stopped. The seat 312B is seated, and the flow paths 311A and 312A of the backflow prevention plate are closed again. That is, in the backflow prevention plates (distribution paths 311A and 312A) according to the present embodiment, the above-described closed state and open state are repeated depending on the supply state (pressure state) of the fluid.

By the way, since the backflow prevention plate shown in FIG. 9 is comprised and functions as mentioned above, the following effects can be acquired.

That is, in the backflow prevention plate according to the present embodiment, even when the circulation paths 311A and 312A are closed, the plate body 314 is not forcibly pressed against the seat 312B by the taxing means 317, but the taxing means is not. A predetermined interval t1 is provided between the upper guide portion 315 and the plate body 314 attached to the 317. Therefore, according to this embodiment, since the plate body 314 (spherical plate body) itself rotates easily by the fluid to distribute | circulate, the plate body 314 can be worn evenly. In the related art, for example, the plate body was pressed against the plate seat by the taxing means so that the plate body could be unevenly worn.

  In addition, in this embodiment, by providing the predetermined space t1, the plate body 314 can be rotated, and the force of the urging means can be made stronger than before. You can get it. In order to strongly suppress uneven wear of the plate body, it is necessary to provide a predetermined limit by the force of the taxing means, and there is a possibility that the closing responsiveness is lowered by this.

In addition, since the backflow prevention plate according to the present embodiment has high closing responsiveness as described above, even when conveying a fluid having a high viscosity, it is possible to effectively carry out quantitative conveyance.

10A and 10B are schematic cross-sectional views showing a second embodiment of the non-return plate according to the embodiment of the present invention, and specifically, FIG. 10A shows a state where the plate body is seated on the seat and the fluid path is blocked. 10B shows a state in which the plate body is opened from the plate seat and the fluid path is opened.

As shown in FIG. 10, the backflow prevention plate according to the present embodiment includes a plate main body 320 and a plate body 324, an upper guide 325 and an upper guide 325 which guide the plate body 324. And the urging means 327 such as an installed spring. In addition, a flow path 320A for circulating the fluid is formed in the plate body portion 320 constituting the backflow prevention plate.

In the present embodiment, the urging means 327 is attached to the upper guide portion 325, and the urging means 327 is used when the backflow prevention plate is in a closed state (see FIG. 10A) (the plate 324 is a seat). At the seat 320B, the predetermined interval t2 (see FIG. 10A) is provided between the taxing means 327 and the plate body 324.

Also in the backflow prevention plate shown in FIG. 10, similarly to the backflow prevention plate described in FIG. 9, when no fluid is supplied, the plate body 324 is seated on the seat 320B and the flow path 320A is closed. Since the urging means 327 has a predetermined interval t2 between the plate member 324, the plate member 324 is not pressed against the seat 320B.

When the fluid is supplied into the non-return plate, as shown in FIG. 10B, the plate body 324 constituting the non-return plate is separated from the seat 320B according to the pressure of the fluid, and at the same time, the force of the urging means 327 is applied. In response to this, the urging means 327 is bent upward, and the flow path 320a of the fluid in the backflow prevention plate is opened.

 After the flow path 320a of the non-return plate is open, when the supply of the fluid stops, the plate body 324 is attached to the seat 320B by the self-weight and the force of the taxable means 327 with the stop of the fluid supply. By being seated, the flow path 320a of the backflow prevention plate is closed again. That is, the backflow prevention plate according to the present embodiment also has the same closed state and open state as described above, depending on the supply state (pressure state) of the fluid, similarly to the backflow prevention plate of FIG. 9.

The backflow prevention plate shown in FIG. 10 is configured such that the taxing means 327 and the plate body 324 are in contact with each other. However, when the plate body 324 is seated on the seat 320B, the plate body 324 and the seat 320B are disposed. The predetermined interval t2 between them is similar to the previous non-return plate (see FIG. 9). Therefore, the same effects as in the case of FIG. 9 can also be obtained with the non-return plate shown in FIG. 10.

In addition, in this FIG. 10, although the guide part of the plate body 324 is not provided in the board | substrate 320B vicinity of the board | substrate main-body part 320, this invention is not limited to this structure, As needed, it is located in the board | substrate 320B vicinity. You may provide a guide part.

11 is a schematic cross-sectional view showing a third embodiment of the non-return plate according to the embodiment of the present invention. Here, the plate body 334 shown by the broken line is seated on the seat 330B, and the state which block | closes the flow path 330a is shown, and the plate body 334 shown by the solid line is separated from the seat 330B, and the flow path 330a is carried out. The state of opening is shown.

As shown in FIG. 11, the non-return plate according to the present embodiment includes a plate main body 330, a plate body 334, and an upper guide part 335 and a plate body 330 that guide the plate body 334. It is comprised including the coil part 339 etc. which were provided in the exterior. Moreover, the flow path 330a for circulating fluid is comprised in the plate main-body part 330 which comprises this backflow prevention plate.

In the non-return plate configured as shown in FIG. 11, the electromagnetic force acting on the plate body 334 is generated in accordance with the power supplied to the coil unit 339, and the plate body 334 is forcibly switched by appropriately switching the polarity of the power supply. ) Can be moved ("up and down movement" in this embodiment, see arrow Y of FIG. 11).

That is, the backflow preventing plate according to the present embodiment is constituted by using a material in which the plate body 334 receives a magnetic force, and the electromagnetic force in the coil portion 339 provided outside the plate body portion 330 is the plate body 334. Act on Therefore, according to this embodiment, the backflow prevention plate with high responsiveness can be obtained by making it possible to appropriately control (invert, etc.) the polarity of the electric current supplied to the coil part 339. In addition, if a capacitor is provided in the power supply line to the coil part 339 (electromagnet) as needed, since a current will be supplied in a short time, it becomes possible to obtain a more responsive backflow prevention plate.

That is, according to the backflow prevention plate which concerns on this embodiment, it becomes possible to forcibly move the board body 334 up and down without using the biasing means, such as a spring, and energizes the coil part 339 at the time of seating. By eliminating, the plate body 334 is not pressed against the seat 330B. Therefore, similarly to Figs. 9 and 10 described above, the backflow preventing plate shown in Fig. 11 can also be removed from uneven wearability of the plate body 334, and quantitative conveyance can be effectively realized even at the time of high-viscosity fluid transfer.

In addition, the reciprocating pump according to the present invention is not limited to the structure shown in Figs. 1 to 7, but may be configured as shown in Figs. In addition, since the reciprocating pump described below is the same as that of the reciprocating pump demonstrated by FIG. 1 to FIG. 7 about the basic structure, the same code | symbol is used for the same component, and here it mainly uses other components. Will be explained.

12 is an external front view of a reciprocating pump according to another embodiment of the present invention, and FIG. 13 is an external side view of the reciprocating pump shown in FIG. 12. 14 is a schematic A-A cross section of FIG. 12, and FIG. 15 is a schematic B-B cross section of FIG. 13.

As described above, the reciprocating pump shown in FIGS. 12 to 15 basically has the same configuration as the reciprocating pump described above, and an auxiliary drive unit is provided to convey fluid to the fluid conveying chamber in the diaphragm driving chamber. There is a difference. So, below, the structure of an auxiliary drive part is mainly demonstrated.

As shown to FIG. 14 and FIG. 15, the reciprocating pump which concerns on this embodiment is a diaphragm suitable to drive the fluid conveyance part 10 which conveys a fluid by reciprocating the diaphragm 1, and the diaphragm 1; Fluid is supplied to the driving force supply part 40 which supplies hydraulic fluid to the oil, the drive part 70 which drives the eccentric cam 42 of this driving force supply part 40, and the fluid conveyance chamber 2a in the fluid conveyance part 10. FIG. It is comprised including the auxiliary drive part 400 etc. which are conveyed.

In this embodiment, the drive part 70, the electric motor 71 which generate | occur | produces a rotational movement, and the gear part 72 etc. for transmitting the rotational force from this electric motor 71 to the drive force transmission shaft 410, etc. It is configured to include. The driving force transmission shaft 410 is configured to supply rotational force to the eccentric cam 42 constituting the driving force supply part 40 and the auxiliary eccentric cam 402 constituting the auxiliary driving part 400. That is, the drive force transmission shaft 411 which concerns on this embodiment, and the 2nd shaft part 412 which rotates the auxiliary eccentric cam 402 are comprised so that it may be integrated.

The auxiliary drive unit 400 includes an auxiliary eccentric cam 402 attached to the second shaft portion 412 which rotates as described above, and an auxiliary diaphragm 401 which is driven in accordance with the movement of the auxiliary eccentric cam 402. (Corresponding to "first auxiliary diaphragm" and "second auxiliary diaphragm" of the present invention) and the like. More specifically, the auxiliary movable body 403 which is in contact with the auxiliary eccentric cam 402 and reciprocates from side to side in accordance with the rotation of the auxiliary eccentric cam 402 and the diaphragm are moved by the movement of the auxiliary movable body 403. It comprises the movable shaft means (1st movable shaft 405, 2nd movable shaft 406) etc. which were attached to the auxiliary movable body 403 so that 1 may reciprocate.

Further, an auxiliary inflow side backflow prevention plate 430 is provided on an upstream side of each diaphragm 1, and the opening and closing of the auxiliary inflow side backflow prevention plate 430 is based on the reciprocating state of each diaphragm 1. The state is controlled. In addition, in this embodiment, the auxiliary leak part 440 is provided so that the fluid more than predetermined amount (pressure) may be conveyed to a fluid conveyance chamber. The auxiliary leak part 440 is provided on the downstream side of each of the backflow prevention plates 430, and is opened and closed to the leak support part 441 and the leak support part 441 to open and close the fluid path. And urging means 442, such as a spring, for urging the opening / closing portion 443 to be in contact with the leak supporting portion 441.

The reciprocating pump according to the present embodiment is configured as described above and functions as follows.

That is, in the reciprocating pump shown in FIG. 12 to FIG. 15, not only the diaphragm 1 reciprocates and conveys the fluid, but also the fluid is introduced into the fluid conveying chamber 2a using the auxiliary drive unit 400. Is returned. More specifically, for example, the diaphragm 1 and the auxiliary diaphragm 401 in the same fluid conveyance path (for example, the diaphragm 1 and the auxiliary diaphragm 401 located on the left side of FIG. 15), When one side discharges, the other side functions to suck.

Here, FIG. 16 shows the pressure waveform of the discharge / suction process of each diaphragm 1,401. FIG. 16A shows the pressure waveform obtained with the diaphragm 1, and FIG. 16B shows the pressure waveform obtained with the auxiliary diaphragm 401. FIG. 16C polymerizes the pressure waveforms of FIG. 16A and FIG. 16B and shows them.

In FIG. 16, the broken line and the solid line show the diaphragm 1 and the auxiliary diaphragm 401 of the same fluid conveyance path, respectively, for example, the diaphragm 1B (right pump in which a solid line is located in the right side of FIG. 15). ) And the auxiliary diaphragm 401B (right pressurized pump), and the broken line has shown the diaphragm 1A (left pump) and the auxiliary diaphragm 401A (left pressurized pump) located in the left side of FIG.

As described above, in the present embodiment, the diaphragm 1 and the auxiliary diaphragm 401 alternately repeat discharge and suction, and at the time of suction of the diaphragm 1, the auxiliary diaphragm 401 is discharged. The required fluid is appropriately conveyed to the inflow conveyance chamber 2a.

When conveying a high viscosity fluid etc., when the pump which drives only the diaphragm 1 cannot carry in the required amount of fluid to the fluid conveyance chamber 2a because the fluid is high viscosity, and cannot carry out fixed quantity conveyance, There was. However, according to this embodiment, even if there is a lack of suction by only the diaphragm 1, by carrying out the auxiliary drive part 400, since the conveyance amount to the fluid conveyance chamber 2a is supplemented, the fluid is fixedly conveyed appropriately. can do.

Moreover, in this embodiment, the auxiliary drive part 400 which functions to replenish fluid appropriately as mentioned above is driven by the drive part 70 which is a drive source which drives the drive force supply part 40. As shown in FIG. That is, according to this embodiment, the auxiliary drive part 400 can be comprised without using a new drive source.

In addition, in this embodiment, when the pressure on the downstream side of the auxiliary inflow side backflow prevention plate 430 becomes more than a predetermined pressure (for example, 0.45 MPa), the auxiliary leak part 440 functions and opens and closes 444. ) Is separated from the leak support portion 441. That is, when the pressure in the urging means 442 is adjusted so that the pressure in the flow path reaches or exceeds a predetermined pressure, the fluid is leaked.

Therefore, according to this embodiment, the pressure in the fluid conveyance chamber 2a does not need to be raised more than necessary, and damage prevention of the diaphragm 1, the auxiliary diaphragm 401, etc. can be aimed at. Moreover, since the predetermined pressure in this auxiliary leak part 440 is determined according to the fixed quantity conveyance amount in the diaphragm 1, ie, it is determined in consideration of there being no oversupply, this auxiliary leak part By providing 440, high-precision quantitative conveyance can be realized.

In addition, this invention is not limited to the said embodiment, It is possible to perform various changes other than the above-mentioned unless the meaning is departed.

For example, the reciprocating pumps shown in Figs. 1 to 7, and 12 to 15 are provided with a plurality of backflow preventing plates 33, 34, 430, respectively, and these backflow preventing plates 33, 34, As 430, there is disclosed a configuration in which the plate body (ball body) is separated from the plate by the fluid pressure, the flow path of the fluid is opened, and the plate body is seated on the plate with its own weight and the flow path is blocked with the decrease in the fluid pressure. However, the present invention is not limited to this configuration, and for example, a reciprocating pump may be configured using a non-return valve as shown in FIGS. 9 to 11 as necessary. All of these backflow prevention plates have high closing responsiveness because the plate body is forcibly moved to the seat side when the flow path is blocked. Therefore, by using such a non-return valve, it is possible to construct a reciprocating pump having the effect of the above-mentioned anti-return plate. Specifically, a reciprocating pump capable of carrying out a quantitative conveyance with high accuracy and a unidirectional wear of the plate body are eliminated, whereby a reciprocating pump capable of long life can be obtained.

As shown in FIG. 11, when constructing a reciprocating pump using the coil part 339 (that is, using an electromagnetic force), it is preferable to use the encoder 500 as shown in FIG. That is, by using this encoder 500, the seating timing etc. of the plate body 334 in a backflow prevention plate are detected, and based on this detection result, the power supply timing and polarity reversal timing etc. to the coil part 339 are controlled. It becomes possible. Here, the seating timing can be grasped | ascertained by detecting the rotation position of the drive force transmission shaft 41 and 410, for example.

As described above, according to the present invention, a reciprocating pump having a gas discharge mechanism capable of properly and automatically discharging gas can be obtained without performing complicated work or the like. In addition, according to the present invention, it is possible to reliably block the flow path, whereby a backflow prevention plate capable of reducing local wear of a ball, a seat, or the like can be obtained without performing a priming liquid or the like. In addition, according to the present invention, a reciprocating pump capable of quantitative conveyance can be obtained even when conveying a fluid with high viscosity.

Claims (10)

delete delete delete delete delete delete delete delete A first diaphragm and a second diaphragm reciprocating to convey fluid, a diaphragm drive chamber provided with the first and second diaphragms, and a driving force supply unit for supplying a driving force for reciprocating the diaphragm, The driving force supply unit includes one eccentric cam and a first piston unit and a second piston unit reciprocating by rotation of the eccentric cam, The driving force of the first and second piston parts is configured to be transmitted to the first and second diaphragms via the hydraulic oil, A first auxiliary diaphragm and a second auxiliary diaphragm reciprocating so as to convey the fluid to the fluid conveyance chamber in the diaphragm drive chamber, and the auxiliary drive conveys the fluid, and the first and second auxiliary diaphragms. An auxiliary eccentric cam for reciprocating the diaphragm, wherein the auxiliary eccentric cam is driven to rotate using a driving force transmission shaft for driving the eccentric cam, The backflow prevention plate is provided in the upstream and downstream of the said 1st and 2nd diaphragm, respectively, The non-return plate includes a main body having a flow path of the fluid, and a plate body installed in the main body to open and close the flow path, and at least one of the main body and the outside of the main body is provided with electromagnet means. And the plate body is made of a magnetic material, and at least one of the energization timing and the polarity switching timing for the electromagnet means is determined in accordance with the opening and closing timing of the flow path to the plate body. Reciprocating pump for conveying. The method of claim 9, A reciprocating motion pump having a capacitor installed in a power supply line to said electromagnet means.

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