JP2001241380A - Reciprocating pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a reciprocating pump of such a constitution as to be capable of preventing pulsation by reducing the number of part items for reducing possibility of liquid leak, and restricting effects of manufacturing errors, assembling errors, etc., in each element. SOLUTION: In this reciprocating pump provided with a diaphragm, and a drive force supply part 40 to drive the diaphragm, the drive force supply part 40 is composed of a single eccentric cam 42, piston parts 43, 44 reciprocated by rotation of the eccentric cam 42, and a regulation means 49 to regulate the positions of the piston parts 43, 44, and the regulation means 49 is composed to have an energization function to energize the piston parts 43, 44 in directions where the eccentric cam 42 is positioned, and a shock absorbing function to absorb deflection between the piston parts 43, 44 caused by change of diagonal distance of the eccentric cam 42.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating pump, and more particularly to a reciprocating pump constituted by using a diaphragm or the like (otherwise, for example, a piston or a plunger) as a reciprocating drive means. is there.

[0002]

2. Description of the Related Art A reciprocating pump for driving a diaphragm to convey a fluid has been known. In such a reciprocating pump, the rotary motion obtained by a driving means such as a motor is converted into a linear reciprocating motion via a cam, and the diaphragm is driven by the linear reciprocating motion.

The above-described reciprocating pump according to the prior art is generally used for so-called metering injection when injecting a chemical or a drug. That is, a reciprocating pump configured using a diaphragm (hereinafter, also simply referred to as a “reciprocating pump”) has conventionally been provided at a location that requires constant-rate transport.

[0004] However, the reciprocating pump having the above-mentioned advantages (the advantage that the fluctuation of the discharge flow rate is small) also has the following problems. The reciprocating pump performs the transfer of the fluid based on the reciprocating motion of the diaphragm,
At this time, the fluid in the pump head is pressurized and pushed out by the forward movement of the diaphragm (hereinafter, referred to as “the fluid”).
This is referred to as the "forwarding process." ), When the diaphragm moves backward, the pressure inside the pump head is reduced and the fluid is drawn in (hereinafter, referred to as a “returning process”). In the reciprocating pump according to the related art, such a relatively fine operation of the forward movement step and the backward movement step is repeated a predetermined number of times in a predetermined time, thereby enabling a constant amount of transport as a whole. Comparing the process with the one return process, there is a large difference in the discharge flow rate between these processes (basically, no discharge is performed in the return process). That is, in the reciprocating pump according to the related art, there is a problem that a pulsation occurs in the transported fluid due to the difference in the discharge flow rate.

Therefore, as a technique for solving such a problem, recently, a reciprocating pump having a structure in which two pump heads each having a diaphragm are provided is known.

FIG. 7 is a schematic perspective view of a conventional reciprocating pump. In FIG. 7, a reciprocating pump 200 includes a first pump head section 210, a second pump head section 220, and these pump head sections 21.
0, 220, and a check valve mechanism (for example, a valve section and a valve seat section) provided on the inflow side and the outflow side of the fluid in each of the pump head sections 210, 220. ) (Not shown). Here, the driving unit 230
For example, it is configured using an electric motor or the like.

[0007] The reciprocating pump 200 is connected to an inflow-side piping section 240 on the liquid inflow side and to an outflow-side piping section 250 on the outflow side. Specifically, the inflow side piping section 2
40, an inflow side flange portion 241, 242 provided in
The pump inflow side flange portions 213 and 223 are connected using bolts and the like, and the outflow side flange portions 251 and 252 provided in the outflow side pipe portion 250 and the pump outflow side flange portions 214 and 224 use bolts and the like. The reciprocating pump 200 and the pipes 240 and 250
And are connected.

Here, each of the connecting parts 211, 212,
One end of each of the pump heads 221 and 222 is
0,220 in a screwed state. Also, at the other end of each of the connecting portions 211, 212, 221, 222,
The flange portions 213, 214, 223, 224 are fixed.

The diaphragm contained in each of the pump heads 210 and 220 constituting the reciprocating pump 200 is such that when one of the diaphragms is in the forward movement step, the other is in the backward movement step, and the other diaphragm is in the backward movement step. Is in the backward movement step, the other diaphragm is constituted in the forward movement step.

That is, according to the reciprocating pump shown in FIG. 7, one diaphragm replaces the other diaphragm.
Since the other diaphragm is driven to complement the one diaphragm, it is possible to obtain a reciprocating pump capable of effectively improving the pulsation which has conventionally been a problem. At this time, in the reciprocating pump according to the prior art, each diaphragm is
Each of the diaphragms is driven using a cam having a phase difference of about 180 °, and for each diaphragm, urging means (spring or the like) is provided to urge the diaphragm in a predetermined direction (usually in a direction opposite to the discharge). ing.

The inside of each pump head constituting the reciprocating pump 200 is constructed, for example, as shown in FIG. FIG. 8 is a longitudinal sectional view of a part of one of the pump heads constituting a reciprocating pump 200 according to the related art.

In FIG. 8, a piston portion 343 as a driving means for reciprocating the diaphragm 301 is fixed to a bearing support portion 348 having a bearing 347, and a support member 35 including the piston portion 343 and the like is provided.
0 and a bearing 349 between the bearing support portion 348.
Is provided, and the biasing means 349 causes the bearing 3
47 contacts the eccentric cam 342 (to the right in the drawing)
It is configured to be biased. In FIG. 8, the pipe portions 240 and 25 through which the carrier fluid flows in the left direction on the drawing.
0 and the like are provided.

According to the reciprocating pump according to the prior art constructed as described above, by rotating the eccentric cam 342 in the direction of arrow R, the diaphragm is moved through the bearing 347, the bearing support 348, the piston 343, and the like. 301 is reciprocated in the arrow Z direction.
At that time, the discharge process of the diaphragm 301 is from the point T0 to the point T1 of the eccentric cam 342, and the stroke distance S from the top dead center S0 at the point T0 to the bottom dead point S1 at the point T1 is determined by the urging means. 349 is the bending distance.

That is, according to the reciprocating pump according to the prior art, the piston 343 and the urging means 349 reciprocate at the interval of the stroke distance S.
The fluid is conveyed by reciprocating the diaphragm 301 appropriately.

[0015]

However, the reciprocating pump according to the prior art has the following problems.

The reciprocating pump 200 according to the prior art is configured to prevent pulsation by using two pump heads 210 and 220. The number of points increases, and the number of sealing portions also increases accordingly.
Therefore, in the reciprocating pump 200 according to the related art, there is a problem that the possibility of liquid leakage increases with an increase in the number of sealing portions.

Further, a reciprocating pump 200 according to the prior art
In the above, as described above, the two pump heads 21
Two eccentric cams, two pistons, two biasing means and the like are provided for driving the respective diaphragms in the cylinders 0 and 220. The reciprocating pump 200 according to the related art is driven to prevent pulsation by appropriately combining these elements (in consideration of the timing of a cam or the like). Therefore, according to the reciprocating pump according to the related art, there are many components, and there is a problem that a manufacturing error and an assembly error of each element greatly affect a driving state thereof.

Further, the reciprocating pump 20 according to the prior art
At 0, the urging means 349 also repeats reciprocating movement (extension and contraction) by the same distance as the stroke distance S of the piston portion 343. Therefore, the urging means 349 using a relatively strong spring or the like is used. And it is difficult to reduce the size of the device.

Therefore, the present invention has been made to solve the problem of the reciprocating pump according to the prior art described above, and is based on the premise that the pulsation can be prevented by reducing the number of parts. It is an object to provide a reciprocating pump that can reduce the possibility of liquid leakage, and
It is an object to provide a reciprocating pump capable of minimizing the effects of manufacturing errors and assembly errors of each element,
It is another object of the present invention to provide a reciprocating pump capable of reducing the reciprocating distance (bending distance) of the urging means and realizing the miniaturization of the device.

[0020]

In other words, the present invention for solving the above-mentioned problems comprises a diaphragm 1,2 which reciprocates in contact with a fluid to be conveyed, and a driving force for driving the diaphragm 1,2. In the reciprocating pump including the supply unit 40, the driving force supply unit 40 includes one eccentric cam 42, and a first piston unit 43 and a second piston unit 44 that reciprocate by the rotation of the eccentric cam 42.
And adjusting means 49 for adjusting the positions of the first and second piston parts 43 and 44.
A biasing function for biasing the eccentric cam 42 in the direction in which the eccentric cam 42 is located; and the first piston portion 43 and the second piston portion 4 due to a change in the diagonal distance of the eccentric cam.
And a buffer function capable of absorbing a shift generated between the first and second members.

According to the reciprocating pump according to the present invention, one eccentric cam 42 is used and two pistons 43 and 44 are used.
Is reciprocated, and based on this, the two diaphragms 1 and 2 are reciprocated. Therefore, even when the two diaphragms 1 and 2 are driven, the number of parts can be reduced as compared with the conventional case. Accordingly, the number of sealing portions can be reduced, so that a reciprocating pump that can reduce the probability of occurrence of liquid leakage or the like can be obtained. In addition, according to the reciprocating pump according to the present invention, as described above, it is possible to reduce the number of components compared to the related art,
It is possible to reduce the probability of occurrence of a manufacturing error of each element as compared with the related art, and it is also possible to reduce an assembly error or the like accordingly. Therefore,
According to the present invention, it is possible to effectively reduce a manufacturing error, an assembly error, and the like of each element, which have adversely affected the driving state of the reciprocating pump in the related art, by reducing the number of parts. . Furthermore, since the reciprocating pump according to the present invention is configured using one eccentric cam 42,
Unlike the conventional case, the two eccentric cams are not required to have the same shape or the like. Further, since one eccentric cam 42 is used,
There is no need for assembling accuracy or the like as before. Therefore, according to the present invention, it is possible to efficiently manufacture and assemble a reciprocating pump (and each element) without going through complicated steps as in the related art.

Further, in the reciprocating pump according to the present invention, the second piston portion 44 is formed in a hollow shape, and the eccentric cam 4 is provided inside the second piston portion 44.
2 and the first piston portion 43, and the adjusting means 49 is provided between an outer surface portion 43a of the first piston portion 43 and an inner surface portion 44a of the second piston portion 44. It is preferable that the first piston 43 and the second piston 44 reciprocate with the adjusting means 49 by the rotation of the eccentric cam 42.

According to this preferred configuration, the rotation of the eccentric cam 42 causes the piston portions 43 and 44 to slide while the adjusting means (position regulating urging means) 49 is sandwiched, and reciprocates repeatedly. As a result, the maximum deflection distance of the adjusting means 49 can be set to be much smaller than that of the related art with respect to the reciprocating distance of the pistons 43 and 44. Accordingly, in the prior art, the stroke distance of the piston and the flexing distance of the biasing means are the same (the biasing means which flexes by the stroke distance of the piston is required). According to this, it is possible to make the amount of deflection of the adjusting means 49 including the urging means or the like smaller than the stroke distance of the piston portions 43 and 44 (for example, about 1/4). Therefore, the adjusting unit 49 can be configured by using a biasing unit having a smaller size and a lower strength than before, so that the driving force supply unit 40, and hence the reciprocating pump, can be downsized. can do.

In the reciprocating pump according to the present invention, the reciprocating directions of the first and second piston portions 43 and 44 are substantially parallel to the biasing direction and the buffering direction of the adjusting means 49. A configuration is preferred.

According to this preferred configuration, it is possible to obtain a reciprocating pump having the above-described various effects and capable of realizing a small size with a relatively simple configuration.

Further, in the reciprocating pump according to the present invention, it is preferable that the adjusting means 49 is constituted by using an urging member composed of a single spring or the like. According to this preferred example, it is possible to easily configure the adjusting means 49 having the various effects described above.

Further, in the reciprocating pump according to the present invention, a first space (in the first piping portion 21) formed between the end face 43a of the first piston portion 43 and one diaphragm 1 is provided. ) And a second space (a space in the second piping portion 22) formed between the end face portion 44 a of the second piston portion 44 and the other diaphragm 2, respectively. Each space is filled with hydraulic oil, and pressure is applied to the hydraulic oil based on the reciprocating motion of the first and second piston portions 43 and 44. It is preferable that the first and other diaphragms 1 and 2 are reciprocated by the pressure.

According to this preferred configuration, it is possible to effectively transmit the driving force from the piston portions 43 and 44 to the diaphragms 1 and 2 and to supply the driving force having the various effects described above. By using the part 40 and the like, it is possible to obtain a reciprocating pump capable of realizing miniaturization and the like.

Further, the present invention relates to a reciprocating pump comprising two diaphragms which reciprocate in contact with a fluid to be conveyed, wherein the liquid contact surface 1a of one diaphragm 1 and the other diaphragm 2 The liquid contact surface 2a is provided so as to be substantially parallel to the liquid contact surface 2a via a pump head 3 having a transport path, and the liquid contact surface 1 of the one diaphragm 1 is provided.
a, a fluid transfer area is formed using the pump head 3 and the liquid contact surface 2a of the other diaphragm 2. Here, the “fluid transfer region” is defined as that the fluid is appropriately leaked by driving the diaphragms 1 and 2 without leaking outside the pipe portion of the pump head 3 connected to the transfer path. It refers to the area that can be transported.

According to the reciprocating pump according to the present invention, the diaphragms 1 and 2 are provided to face each other with the pump head 3 interposed therebetween. In comparison, it is possible to greatly reduce the number of parts when configuring the pump.
Therefore, as the number of components decreases, the number of sealing portions can be reduced as compared with the conventional case, and the possibility of liquid leakage can be reduced by the reduced number of sealing portions. Further, according to the reciprocating pump according to the present invention, since the pump head 3 is provided between the opposed diaphragms 1 and 2, the movement of one diaphragm has an adverse effect on the other diaphragm. Without this, each diaphragm can appropriately carry out a predetermined movement. Therefore, according to the present embodiment, it is possible to obtain a reciprocating pump capable of appropriately maintaining the discharge flow rate of each diaphragm and effectively preventing the pulsation of the transport fluid.

In the reciprocating pump according to the present invention, the diaphragms 1 and 2 and the pump head 3
It is preferable that the transfer fluid flow block 25 configured by using the liquid can be separated without leaking the fluid from the fluid transfer area. That is, the transported fluid is not in contact with the surfaces of the diaphragms 1 and 2 on the back side of the liquid contact surfaces 1a and 2a. It is preferable that the structure can be separated from a driving force supply unit or the like for driving each of the diaphragms 1 and 2 without causing leakage.

According to this preferred configuration, the maintenance process can be performed efficiently. That is, according to the reciprocating pump according to the present invention, the pipe section and the like are removed without disassembling the transport fluid flow block 25 and the maintenance of the driving force supply section (for example, the eccentric cam,
(Eg, replacement of the position regulating urging means), so that the maintenance process can be performed without disassembling and assembling the two pump heads as in the related art. Therefore, it is possible to obtain a reciprocating pump excellent in maintainability, capable of performing maintenance of the driving force supply unit and the like without previously removing the carrier fluid flowing in the carrier fluid circulation block 25.

[0033]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a schematic sectional view of a reciprocating pump according to an embodiment of the present invention. Also, FIG.
FIG. 2 is an enlarged view of a fluid transporting part constituting the reciprocating pump of FIG. 1, and FIG.
(B) shows a disassembled state. Further, FIG.
FIG. 4 is a sectional view taken along the line III-III, and FIG.
FIG. 4 is a sectional view taken along a line IV. Hereinafter, the reciprocating pump according to the present embodiment will be described in detail with reference to these drawings.

The reciprocating pump according to the present embodiment comprises a fluid transport unit 10 for transporting a fluid by reciprocating diaphragms (first diaphragm 1 and second diaphragm 2), and diaphragms 1 and 2. Driving force supply unit 4 that supplies hydraulic oil at appropriate timing to drive
0, and a driving unit 70 for driving the eccentric cam of the driving force supply unit 40 and the like.

The fluid transfer section 10 constituting the reciprocating pump according to the present embodiment is specifically configured as shown in FIGS. 1, 2 and 4. In these drawings, a fluid transport unit 10 includes a first diaphragm 1, a second diaphragm 2, a pump head 3, and a diaphragm support (a second diaphragm support) that sandwiches and supports the diaphragms 1 and 2 together with the pump head 3. One diaphragm support 4 and a second diaphragm support 5) and the liquid contact surfaces 1 of the diaphragms 1 and 2
a and 2a sides, between the pump head 3 and each of the diaphragms 1 and 2, a carrier fluid circulating portion (first carrier fluid circulating portion 6 and second carrier fluid circulating portion 7); , 2 (the back surfaces of the liquid contact surfaces 1a, 2a) and between the respective diaphragm supports 4, 5 and the respective diaphragms 1, 2 (a first hydraulic oil circulating portion). 8 and a second hydraulic oil circulating section 9) and a pipe section (a first pipe section 21 and a second pipe section 22) for transmitting a driving force from a driving force supply section 40 (described later). It is configured using the formed hydraulic oil supply units (the first hydraulic oil supply unit 11 and the second hydraulic oil supply unit 12) and the like.

Here, each of the diaphragms 1 and 2 has, for example, a corrugated shape, a curved surface shape, or the like in cross section, but in FIG. The typical cross-sectional shape is omitted.
The pump head 3 is formed with transport paths 3A and 3B for transporting the fluid. On the inflow side and the outflow side of these transport paths 3A and 3B, check valves (inflow side check valve 23 and outflow side check valve 24) are provided, respectively, as shown in FIG. Here, each check valve 23, 24
Is configured using two ball checks. Further, between each of the diaphragms 1 and 2 and the pump head 3, there is provided a transporting fluid flow section 6 or 7. A plurality of through-holes are formed in the transfer fluid circulation portions 6 and 7,
Positive pressure / negative pressure due to the reciprocating motion of the diaphragms 1 and 2 are transmitted to the transport paths 3A and 3B via the through holes. Then, the check valves 23 and 24 are opened and closed by the reciprocating motion of the diaphragms 1 and 2 (by the positive and negative pressures), and the fluid is conveyed.

Diaphragm supports 4, 5 are provided on the back side of each of the diaphragms 1, 2 via hydraulic oil circulating sections 8, 9. The diaphragm supports 4, 5 and the pump head 3 Diaphragms 1 and 2 are clamped and fixed. The diaphragm supports 4 and 5 and the pump head 3 are fastened by fastening means such as bolts. A plurality of through-holes are formed in the hydraulic oil flow sections 8 and 9, and the hydraulic oil supplied from the driving force supply section 40, which will be described later, passes through the through-holes to the rear surfaces of the diaphragms 1 and 2. Will be sent and discharged. Hydraulic oil supply units 11 and 12 communicating with the driving force supply unit 40 are attached to the hydraulic oil supply units 8 and 9.
Reference numerals 1 and 12 are fastened to the hydraulic oil flow sections 8 and 9 by bolts or the like.

Next, the driving force supply unit 40 constituting the reciprocating pump according to the present embodiment will be described in detail with reference to FIGS.
And FIG. In these drawings, a driving force supply unit 40 includes a driving force transmission shaft 41 that transmits a driving force from a driving unit 70 described later, an eccentric cam 42 attached to the driving force transmission shaft 41, and an eccentric cam 42. A piston part (first piston part 43 and second piston part 44) that reciprocates according to the movement, and a first rotating shaft supported by inner rings of bearings 47, 47 in the first piston part 43. 45, and a second rotating shaft 4 supported by inner rings of bearings 48, 48 in the second piston portion 44.
6 and the first piston part 4 in the second piston part 44
3 and the second piston portion 44 are appropriately urged to rotate the respective rotation shafts 45, 4 provided in the respective piston portions 43, 44.
It is configured by using a position regulating urging means 49 as an adjusting means functioning to bring the 6 into contact with the eccentric cam 42, and a casing part 50 or the like including these elements. In the driving force supply section 40 having the above-described elements, the inner wall of the casing section 50 and the piston sections 43 and 44 are provided.
The working space is filled with hydraulic oil.

In the driving force supply section 40 according to the present embodiment, the second piston section 44 is formed in a hollow shape. That is, the second piston portion 44 has
Driving force transmission shaft 41, eccentric cam 42, first piston portion 4
3, the bearing 48, the position regulating urging means 49 and the like are formed so as to be able to be included. A position regulating urging means 49 is sandwiched between an inner wall portion (inner surface portion) 44a of the second piston portion 44 and an outer wall portion (outer surface portion) 43a of the first piston portion 43. That is, the first and second piston portions 43 and 44 are urged by the position regulating urging means 49 in the direction in which the eccentric cam 42 is located. In other words, the position regulating urging means 49
As a result, the first rotating shaft 45 in the first piston portion 43
And a second rotation shaft 45 in the second piston portion 44,
It is appropriately urged to always contact the outer peripheral surface of the eccentric cam 42.

Further, each casing 2 is provided in the casing 50.
A supply port (a first supply port 51 and a second supply port 52) for hydraulic oil is formed so as to communicate with the first and second ports 22. Then, from the end faces 43a, 44a of the pistons 43, 44, through the supply ports 51, 52, the pipes 21, 22, etc.,
The space formed between each of the diaphragms 1 and 2 is configured in a substantially sealed state, and this space is filled with hydraulic oil. Therefore, in this embodiment,
Positive pressure / negative pressure acts on the hydraulic oil in accordance with the movement of each of the piston portions 43 and 44, and this pressure fluctuation causes each of the supply ports 5.
Hydraulic oil is circulated through 1 and 52. The hydraulic fluid causes the diaphragms 1 and 2 to reciprocate.

Next, the drive section 70 constituting the reciprocating pump according to the present embodiment is configured as shown in FIGS. In these drawings, a driving unit 70 is configured using an electric motor 71 that generates a rotational motion, a gear unit 72 for transmitting the rotational force from the electric motor 71 to the driving force transmission shaft 41 described above, and the like. Have been.

As described above, the reciprocating pump according to the present embodiment is configured by using the fluid transfer unit 10, the driving force supply unit 40, the driving unit 70, and the like, and functions as follows.

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

Next, the eccentric cam 42 is rotated by the driving force transmitting shaft 41, and the rotation of the eccentric cam 42 causes the first and second piston portions 43 and 44 to reciprocate. Here, based on the above-described configuration, the first piston portion 43 and the second piston portion 44 reciprocate integrally by one eccentric cam 42. Then, a predetermined force and a predetermined pressure act on the hydraulic oil by the reciprocating motion of the pistons 43 and 44, and the hydraulic oil is sent to and discharged from the pipes 21 and 22 through the supply ports 51 and 52. The Rukoto.

Next, the diaphragms 1 and 2 reciprocate at an appropriate timing based on the hydraulic oil flowing through the pipe sections 21 and 22, and the movement of the diaphragms 1 and 2 causes the inflow-side check valve 23 to move. And the outflow side check valve 24 is operated, and the desired liquid is conveyed.

The reciprocating pump according to the present embodiment configured and functioning as described above has the following features based on at least one of the configuration and the function.

As described above, the driving force supply section 40 constituting the reciprocating pump according to the present embodiment includes the casing 50.
Eccentric cam 42, piston portions 43, 44 provided in
And the position regulating urging means 49 and the like. Therefore, in the present embodiment, even when the two diaphragms 1 and 2 are driven, two pump heads each having a cam, a spring, and the like are used as in the related art (see FIGS. 7 and 8). No need to provide.
That is, according to the present embodiment, the two pistons 43 and 44 are reciprocated using one eccentric cam 42, and the two diaphragms 1 and 2 are reciprocated based on this.

Therefore, according to the present embodiment, even when the two diaphragms are driven, the number of parts can be reduced as compared with the conventional case, and accordingly, the number of sealing portions can be reduced. Therefore, a reciprocating pump that can reduce the probability of occurrence of liquid leakage or the like can be obtained.

The reciprocating pump according to the present embodiment
As described above, the number of constituent elements can be reduced as compared with the related art, so that the occurrence probability of a manufacturing error of each element can be reduced as compared with the related art, and the assembly error and the like can be reduced accordingly. Therefore, according to the present embodiment, it is possible to effectively reduce the manufacturing error and the assembly error of each element, which have adversely affected the driving state of the reciprocating pump in the related art, by reducing the number of parts. It becomes possible.

In the conventional case, two eccentric cams are connected to one another.
It is necessary to mount it out of phase by 80 °.
Since the mounted eccentric cams need to have the same shape, high precision is required for manufacturing errors and assembly errors. Therefore, the steps of manufacturing and assembling are very complicated. However, in the present embodiment, since one eccentric cam is used, it is not required that the two eccentric cams have the same shape as in the related art.
In addition, since it is one eccentric cam, there is no need for assembling accuracy or the like as in the related art. Therefore, according to the present embodiment, it is possible to efficiently manufacture and assemble the reciprocating pump (and each element) without going through complicated steps as in the related art.

Further, the size of the reciprocating pump according to the present embodiment can be reduced as compared with the conventional one for the following reasons.

FIG. 5 shows a driving force supply unit 4 according to this embodiment.
0 shows the driving state of the second piston portion 44 constituting 0. Here, FIG. 5A shows a state where the second piston portion 44 is at the bottom dead center, and FIG. 5B shows a state where the second piston portion 44 is at the top dead center. . FIG.
At a predetermined position (an appropriate position that does not particularly fluctuate due to the rotation and reciprocation of the eccentric cam 42 and the like, for example, the wall surface of the casing 50).
To the bottom dead center distance P1 and top dead center distance P, respectively.
It is 2.

In the reciprocating pump according to this embodiment, the difference in the distance between the bottom dead center and the top dead center in FIG.
The stroke distance P of the second piston part 44 in the reciprocating pump is P (P = P2−P1). Here,
Although omitted, in a state where the phase is shifted by 180 °, the first piston portion 43 also reciprocates at the same stroke distance P.

In this embodiment, the state where the second piston portion 44 is at the bottom dead center as shown in FIG. 5A is defined as "eccentric cam angle 0 °", and the second piston portion 44 is pushed in. By rotating the eccentric cam 42 in the direction, for example, when the eccentric cam 42 rotates 210 °, the second piston portion 44 is in a state of being at the top dead center. Note that the rotation angle of the eccentric cam 42 can be appropriately changed based on the shape of the eccentric cam and the like.

FIG. 6 shows an operation state of the position regulating urging means 49 constituting the driving force supply section 40 according to the present embodiment. Here, FIG. 6A shows a state in which the position regulating urging means 49 is most contracted (minimum length R1).
FIG. 6B shows a state (maximum length R2) in which the position regulating urging means 49 is extended most.

In the reciprocating pump according to the present embodiment, the difference between the distance between the contracted state (minimum length R1) and the expanded state (maximum length R2) in FIG. Is the maximum deflection distance R (R = R2−R1).

That is, in the reciprocating pump according to this embodiment, the first piston 43 and the second piston 4
4 and the position regulating urging means 49 is
With the rotation of No. 2, it expands and contracts by the maximum bending distance R while sliding with the piston portions 43 and 44.

As is clear from FIGS. 5 and 6, according to this embodiment, the reciprocating distance P of the piston portion is
The maximum deflection distance R of the position regulating urging means 49 is a considerably small distance. In the present embodiment, P: R =
It is about 4: 1.

On the other hand, in the prior art, as described above, the stroke distance of the piston and the distance that the urging means bends are the same (the urging means that bends by the stroke distance of the piston is required). According to the present embodiment, however, according to the present embodiment, the amount of deflection R of the position regulating urging means 49 is determined.
Is about 1/4 of the stroke distance P.

Therefore, according to the present embodiment, it is possible to configure the position regulating urging means 49 by using urging means which is smaller in size than the conventional one and does not need the strength as in the prior art. The miniaturization of the part 40 and thus the reciprocating pump can be realized.

The position regulating urging means 49 constituting the reciprocating pump according to this embodiment is formed by using urging means such as a coil spring.
The first piston portion 43 and the second piston portion 44 are effectively urged in the direction in which the eccentric cam 42 is located (in the direction in contact with the eccentric cam 42), so that the piston portions 43 and 44 and the eccentric cam 42 The positional relationship can be appropriately maintained.

Further, since the position regulating urging means 49 is formed by using an urging means such as a coil spring, the position of each piston 43, Even when a force acts in a direction in which a displacement occurs between the eccentric cam 44 and the eccentric cam 42, the displacement is effective because of the urging means (because the coil spring or the like has an elastic force together with the urging force). Can be absorbed. That is, the position regulating urging means 49 is used to
And the like.

As described above, according to the present embodiment, a reciprocating pump can be constituted by using a small urging means having a smaller amount of bending than the conventional one. FIG. 3 shows a configuration that can be configured using such a small urging means.
As shown in the figures, the driving force supply unit 40 according to the present embodiment
This is because the piston portions 43 and 44 are configured to repeat reciprocation while sliding.

That is, according to the reciprocating pump according to the present embodiment, the second piston portion 44 is formed in a hollow shape, and the eccentric cam 42 is provided inside the second piston portion 44.
And a first piston 43, and a position regulating urging means 49 serving as an adjusting means between an outer surface 43a of the first piston 43 and an inner surface 44a of the second piston 44.
Is provided, the rotation of the eccentric cam 42 causes the first piston portion 43 and the second piston portion 44 to reciprocate with the position regulating urging means 49. That is, the rotation of the eccentric cam 42 causes the position regulating urging means 4 to rotate.
Since the piston portions 43 and 44 repeat the reciprocating motion while sliding while holding the position 9, the size of the position regulating urging means 49 can be reduced as described above.

The reciprocating pump according to the present embodiment is
Hydraulic oil is provided between each of the piston portions 43 and 44 and each of the diaphragms 1 and 2, and each of the piston portions 4
Although the configuration for transmitting the driving force from the pistons 43 and 44 to the respective diaphragms 1 and 2 has been described, the present invention is not limited to this configuration. Can be transmitted to each of the diaphragms 1 and 2. Therefore, for example, each piston unit and each of the diaphragms 1 and 2 may be configured to be mechanically interlockable. Further, in the reciprocating pump according to the present embodiment, the case where the diaphragm is used for the liquid contact part has been described, but the present invention is not limited to this configuration, and for example, a piston or a plunger or the like may be used for the liquid contact part. A reciprocating pump may be provided.

The reciprocating pump according to the present embodiment
It has two diaphragms 1 and 2, each of which has a wetted surface 1
a, 2a are provided so as to be substantially parallel with each other via the transport fluid flow parts 6, 7 and the pump head 3. further,
Hydraulic oil circulating sections 8,
Diaphragm supports 4 and 5 are provided via 9. That is, according to the present embodiment, the transport fluid flow block 25 is formed using the pump head 3, the diaphragm supports 4, 5, the transport fluid flow portions 6, 7, the hydraulic oil flow portions 8, 9, and the like. (See FIG. 2B). Note that the transport fluid flow block 25 is not limited to the above configuration, and may have another configuration as long as the transport fluid does not leak. For example, the diaphragms 1 and 2 may be fixed to the pump head 3, and these members may be used to form a transport fluid flow block.

In the transport fluid flow block 25 configured as described above, the space between the first diaphragm 1 and the second diaphragm 2 is formed as a closed space.
As shown in (b), even when the hydraulic oil supply units 11 and 12 are removed, the carrier fluid does not leak from the inside of the carrier fluid flow block 25.

Therefore, according to the reciprocating pump according to the present embodiment configured as described above, it is possible to efficiently perform maintenance processing. That is, according to the reciprocating pump according to the present embodiment, as shown in FIG.
Since the pipe sections 21, 22 and the like can be removed and maintenance of the driving force supply section 40 (for example, replacement of the eccentric cam 42 and the position regulating urging means 49) can be performed, two pumps can be used as in the related art. Maintenance processing can be performed without disassembling and assembling the head. Therefore,
In the present embodiment, it is possible to perform maintenance or the like of the driving force supply unit 40 without previously removing the carrier fluid flowing through the carrier fluid distribution block 25.
A reciprocating pump excellent in maintenance can be obtained.

The reciprocating pump according to the present embodiment also
Although two diaphragms are provided as in the related art, according to the present embodiment, since the two diaphragms are provided in one block (the transfer fluid flow block 25), two independent diaphragms are provided as in the related art. As compared with the case where the pump head is provided, it is possible to greatly reduce the number of parts when configuring the pump. Therefore, as the number of components decreases, the number of sealing portions can be reduced as compared with the conventional case, and the possibility of liquid leakage can be reduced by the reduced number of sealing portions.

Further, according to the reciprocating pump according to the present embodiment, since the pump head 3 is provided between the opposed diaphragms 1 and 2, the movement of one diaphragm adversely affects the other diaphragm. Without affecting
Each of the diaphragms can appropriately perform the predetermined movement. Therefore, according to the present embodiment, it is possible to obtain a reciprocating pump capable of appropriately maintaining the discharge flow rate of each diaphragm and effectively preventing the pulsation of the transport fluid.

[0072]

As described above, according to the present invention, it is possible to obtain a reciprocating pump in which the number of parts is reduced and the possibility of liquid leakage is reduced on the premise that the pulsation can be prevented. In addition, it is possible to obtain a reciprocating pump capable of minimizing the effects of manufacturing errors and assembly errors of each element, and further reduce the bending distance of the urging means to reduce the size of the device. Can be obtained.

[Brief description of the drawings]

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

FIG. 2 is an enlarged view of a fluid transporting section constituting the reciprocating pump of FIG. 1;

FIG. 3 is a sectional view taken along line III-III of FIG. 1;

FIG. 4 is a sectional view taken along line IV-IV of FIG.

FIG. 5 is a schematic view showing a driving state of a second piston unit constituting the driving force supply unit according to the embodiment;

FIG. 6 is a schematic diagram showing an operation state of a position regulating urging unit constituting the driving force supply unit according to the embodiment;

FIG. 7 is a schematic perspective view of a reciprocating pump according to the related art.

8 is a partial vertical sectional view of one of the pump heads constituting the reciprocating pump shown in FIG. 7;

[Explanation of symbols]

1 ... first diaphragm, 2 ... second diaphragm, 3
... Pump head, 4 ... First diaphragm support, 5 ...
2nd diaphragm support, 6 ... first transport fluid circulation section, 7 ... second transport fluid circulation section, 8 ... first hydraulic oil circulation section, 9 ... second hydraulic oil circulation section, 10 ... fluid Transport unit, 11
... first hydraulic oil supply unit, 12 ... second hydraulic oil supply unit, 2
DESCRIPTION OF SYMBOLS 1 ... 1st piping part, 22 ... 2nd piping part, 23 ... Inflow side check valve, 24 ... Outflow side check valve, 25 ... Carrier fluid distribution block, 40 ... Driving force supply part, 41 ... Driving force Transmission shaft, 42
... Eccentric cam, 43 ... First piston part, 44 ... Second piston part, 45 ... First rotation axis, 46 ... Second rotation axis,
47, 48 ... bearing, 49 ... position regulating urging means, 5
0: casing, 51: first supply port, 52: second supply port, 70: drive unit

Claims (5)

[Claims] 1. A reciprocating pump comprising: 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 that reciprocate by the rotation of the eccentric cam, and adjusting means for adjusting the positions of the first and second piston portions. Means for urging the first and second piston portions in a direction in which the eccentric cam is located; and a first piston portion and the second piston portion that are caused by a change in a diagonal distance of the eccentric cam. A reciprocating pump having a shock absorbing function capable of absorbing a displacement generated between the two piston portions. 2. The second piston portion is formed in a hollow shape, the eccentric cam and the first piston portion are provided inside the second piston portion, and the first piston portion is provided. The adjusting means is provided between an outer surface of the second piston part and an inner surface of the second piston part, and the rotation of the eccentric cam causes the first piston part and the second piston part to be adjusted by the adjusting means. The reciprocating pump according to claim 1, which reciprocates with the pump. 3. The reciprocating pump according to claim 1, wherein a reciprocating direction of the first and second pistons is substantially parallel to a biasing direction and a buffering direction of the adjusting unit. 4. The reciprocating pump according to claim 3, wherein said adjusting means is constituted by using an urging member comprising one spring or the like. 5. A first space formed between an end face of the first piston portion and one diaphragm, and a first space formed between an end face of the second piston portion and another diaphragm. And each of the second spaces is substantially closed, and each of the spaces is filled with hydraulic oil, and the hydraulic oil is filled based on reciprocation of the first and second piston portions. The reciprocating pump according to any one of claims 1 to 4, wherein a pressure acts on the first and other diaphragms by the pressure.