KR101823607B1 - Plunger type pulse free metering pump - Google Patents

Abstract

The present invention relates to a plunger type pulseless metering pump and, more specifically, relates to a plunger type pulseless metering pump allowing a plunger to perform sliding motion by motion of three cams with a phase difference of 120, so as to supply a predetermined amount of liquid while the fluid realizes a pulseless waveform in an inlet/outlet pipe. According to the present invention, since the pulseless metering pump sequentially operates first, second, and third plungers, a flow rate is realized in a pulseless waveform in the inlet/outlet pipe; thereby stably transferring the fluid without vibration and also removing attachment of an air chamber to buffer a pulse in an existing metering pump, thus providing an installation cost saving effect and an advantage capable of simplifying pipeline. According to the present invention, the pulseless metering pump comprises first, second, and third operation units including a head unit, a cylinder unit, and a motion unit.

Description

[0001] The present invention relates to a plunger type pulse free metering pump,

The present invention relates to a plunger-type pulsating pump, and more particularly to a plunger type pulsating pump which is capable of performing a sliding motion of a plunger by three cams having a phase difference of 120 degrees, thereby forming a pulsating wave in a suction / Type pulsating pump.

 In general, a metering pump sucks liquid through a suction pipe and discharges it through a discharge pipe, which is used in various fields. Particularly in certain fields where precise amounts of fluid must be supplied at regular intervals, such as wastewater treatment, water treatment, and physics, etc., metering pumps are inevitably used.

A general metering pump is composed of a storage tank containing fluid to be supplied, an eccentric cam rotated by a motor, a diaphragm cyclically reciprocating by a pumping shaft periodically contacting the eccentric cam, A suction pipe connected to the tank, and a discharge pipe coupled to the upper portion of the diaphragm to transfer the liquid to a desired place.

Generally, the flow waveform of the suction / discharge pipe of the metering pump using the eccentric cam is repeatedly sucked and discharged, and has a sinusoidal wave, which causes pulsation in the suction / discharge pipe.

Further, in order to remove the pulsation generated as described above, a pulsation prevention device such as an air chamber or a damper must be additionally installed, which complicates the construction of the metering pump and increases the installation cost.

SUMMARY OF THE INVENTION Accordingly, the present invention has been made to solve the above-mentioned problems. Accordingly, it is an object of the present invention to provide a method and a device for controlling a plunger in which a plunger makes a sliding motion by three cams having a phase difference of 120 degrees, The present invention provides a plunger type pulsating flow rate metering pump.

According to an aspect of the present invention,

(i) a head portion including a suction port formed at an upper / lower end thereof, a discharge port, and a pressure chamber connecting the suction port and the discharge port;

(ii) a cylinder portion connected to the head portion, the plunger slidingly moving in the axial direction of the cylinder; And

(iii) a first guide piston having one end connected to the plunger and the other end connected to the first roller follower; A second guide piston connected to the first guide piston by a hanger rod and reciprocating in a cylinder axial direction integrally with the first guide piston; A second roller follower connected to one end of the second guide piston in a first guide piston direction; And a cam fixed to the camshaft, the camshaft being perpendicular to the axial direction of the cylinder, the camshaft being in contact with the first roller follower and the second roller follower,

A first driving unit including a first driving unit,

And a second driving unit and a third driving unit, each of which includes the same configuration of the first driving unit and is positioned horizontally with respect to the first driving unit,

The cams of the first, second, and third driving units share the camshaft, and the angular difference between the center line of the cam passing through the center of the camshaft and the cylinder axis is 120 deg. Pulsation metering pump is fixed to the camshaft so as to be able to rotate the camshaft.

In the pulsating pump of the present invention, since the first, second and third plungers are sequentially driven, the flow rate in the suction / discharge pipe is realized as a non-pulsating waveform, so that the fluid is stably transported without vibration, There is no need to attach an air chamber for alleviating pulsation, thereby reducing installation cost and simplifying piping facilities.

1 is a side view of a pulsating flow rate metering pump according to an embodiment of the present invention,
2 is a plan view of a pulsating flow rate measuring pump according to an embodiment of the present invention,
3 is a schematic view showing a state in which the cam 135 rotates with the first and second roller followers 132a and 132b and the cam 135 being in a grounded state,
4 is a graph showing the relationship between the position of the plunger 122 and the position of the plunger 122 relative to the rotation of the cam 135, (A: first drive unit, B: first drive unit to third drive unit)
5 is a diagram simulating the discharging and sucking processes of the pulsating flow rate measuring pump according to the present invention (A: discharging process, and B: sucking process).

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings. In order to clearly explain the present invention, parts not related to the description are omitted, and similar parts are denoted by similar reference numerals throughout the specification, and detailed configuration directions will be described with reference to the drawings. Also, throughout the specification, when an element is referred to as "comprising ", it means that it can include other elements, not excluding other elements, unless specifically stated otherwise.

The inventor of the present invention has conducted intensive studies to solve the problem of a conventional metering pump in which a pulsation prevention device such as an air chamber and a damper has to be additionally installed in order to remove pulsation, Type plunger type pulsating pump capable of supplying a predetermined amount of fluid by making the plunger slide in the direction of movement of the three cams having the pulsation waveform of the suction / Thereby completing the invention.

Accordingly, the pulsating pump of the present invention is characterized in that (i) the head portion includes a suction port formed at the upper / lower end thereof, a discharge port, and a pressure chamber connecting the suction port and the discharge port;

(ii) a cylinder portion connected to the head portion, the plunger slidingly moving in the axial direction of the cylinder; And

(iii) a first guide piston having one end connected to the plunger and the other end connected to the first roller follower; A second guide piston connected to the first guide piston by a hanger rod and reciprocating in a cylinder axial direction integrally with the first guide piston; A second roller follower connected to one end of the second guide piston in a first guide piston direction; And a cam fixed to the camshaft, the camshaft being perpendicular to the axial direction of the cylinder, the camshaft being in contact with the first roller follower and the second roller follower,

A first driving unit including a first driving unit,

And a second driving unit and a third driving unit, each of which includes the same configuration of the first driving unit and is positioned horizontally with respect to the first driving unit,

The cams of the first, second, and third driving units share the camshaft, and the angular difference between the center line of the cam passing through the center of the camshaft and the cylinder axis is 120 deg. Pulsation metering pump is fixed to the camshaft so as to be able to rotate the camshaft.

Hereinafter, the non-pulsating metering pump according to the present invention will be described in detail with reference to examples.

1 is a side view of a pulsating flow rate measuring pump according to an embodiment of the present invention, and FIG. 2 is a plan view of a pulsating flow rate measuring pump according to an embodiment of the present invention.

Referring to FIGS. 1 and 2, the pulsating pump of the present invention includes a first driving part 100, a second driving part 200, and a third driving part 300. All the components constituting the first driving part 100, the second driving part 200 and the third driving part 300 are the same, and each is installed in a horizontal direction. However, the angles at which the cams 135 included in the respective driving units are fixed to the camshaft 136 are different, and details thereof will be described later.

The first driving part includes a head part 110, a cylinder part 120 and a moving part 130.

The head 110 includes a suction pipe 111 as a passage through which the fluid flows, an inlet 112 for controlling the flow of the fluid flowing through the suction pipe, a moving pipe 113 for moving the fluid introduced into the head through the suction port, A discharge port 114 for controlling the fluid to be discharged through the moving pipe 113, a discharge pipe 115 for discharging the fluid discharged through the discharge port 114, and a plunger 122, And a pressure chamber 116 in which the pressure of the fluid in the portion 110 is regulated.

The suction port 112 includes a suction check ball 112a and a suction check ball seat 112b and when the suction check ball 112a is in contact with the suction ball seat 112b, When the suction check ball 112a rises and separates from the suction check ball seat 112b, the fluid can flow into the head through the suction check ball seat 112b.

The discharge port 114 includes a discharge check ball 114a and a discharge check ball seat 114b and is provided on the same principle as the suction check ball 112a and the suction check ball seat 112b of the suction port 112, Can be controlled.

The suction port 112 and the discharge port 113 are connected to each other by a moving pipe 113 so that the fluid can move and the moving pipe 113 can be connected to the pressure chamber 116.

The pressurizing chamber 116 is a space in which the plunger 122 serves as a moving passage and the fluid flowing into the head through the inlet 112 and the moving tube 113. The plunger 122 slides in the direction of the head 110 And may act to generate a pressure in the fluid staying in the pressurizing chamber 116 and the moving tube 113 when exercising.

The cylinder portion 120 includes a cylinder wall 121 and a plunger 122.

The cylinder wall 121 is connected to the head part 110 and the moving part 130 and can serve as a passage through which the plunger 122 moves.

The moving part 130 serves to cause sliding movement of the plunger 122 in the direction of the cylinder axis 120a and includes a first guide piston having one end connected to the plunger 122 and the other end fixed with a first roller follower, A second guide piston 131b connected to the first guide piston 131a by a hanger rod 134 to integrally reciprocate and having a second roller follower fixed to one end thereof, A first roller follower 132a fixed at one end of the guide piston by a first roller follower shaft 133a so as to rotate in place and fixed at one end of the second guide piston by a second roller follower shaft 133b, A cam 135 fixed to the camshaft 136 which is horizontal to the paper surface and installed in a direction perpendicular to the cylinder axis 120a and connected to the motor so that the camshaft 136 A motor < RTI ID = 0.0 > It is grounded and coupled 137 and the camshaft 136 includes a cam shaft bearing 138 that facilitates the rotational movement of the camshaft 136. The

The upper end of the first guide piston 131a may be provided with a groove on which the hanger band 134a can be mounted and the upper end of the second guide piston 131b may be formed with a groove Can be formed. The hanger band 134b and the hanger pipe 134a can be respectively mounted on the upper grooves of the first guide piston and the second guide piston and are connected to the first guide piston and the second guide piston by the connecting pin 134e, Can be fixed.

The hanger rod 134 includes a hanger pipe 134a, a hanger base 134b, a spring 134c, a nut 134d and a connecting pin 134e. The hanger base 134b is inserted into the hanger pipe 134a and then can be firmly coupled to the hanger pipe 134a by the nut 134d and is inserted between the hanger base 134b and the nut 134d The spring 134c can be inserted to compensate for the mechanical step or the design error. After the hanger rod 134 is engaged with the first guide piston 131a and the second guide piston 131b, the first guide piston 131a and the second guide piston 131b reciprocate integrally can do.

3 is a schematic diagram showing the manner in which the cam 135 rotates with the first and second roller followers 132a and 132b and the cam 135 being in a grounded state. When the angle of the reference line parallel to the cylinder axis 120a passing through the rotation center 135d of the cam 135 at a specific point in time is assumed to be 0 DEG, at another point in time after the rotation of the cam 135, The angle formed with the cylinder axis 120a is shown in Fig. The positions of the first roller follower 132a and the second roller follower 133b shown in FIG. 3 are the relative positions at the time when the cam 135 rotates, and the first and second roller followers 132a, Is fixed.

Referring to FIGS. 1 and 3, a first roller follower 132a fixed to one end of the first guide piston 131a and capable of rotating in place can be fixed to one end of the second guide piston 131b, The second roller follower 132b is grounded with the outer surface of the cam 135. When the cam 135 rotates by the rotation of the cam shaft 136, the first and second roller followers 132a , 132b can also rotate in place along the outer surface of the cam 135. [ At this time, the distance L between the first roller follower shaft 133a fixing the first roller follower and the second cam follower shaft 133b fixing the second roller follower is kept constant at any moment The outer surface of the cam 135 is designed. The angle between the straight line connecting the rotation center 135a of the cam and the first roller follower shaft 133a and the straight line connecting the rotation center 135a of the cam and the second roller follower shaft 133b, lt; RTI ID = 0.0 > 180 C. < / RTI >

On the other hand, the camshaft 136 is installed horizontally with the ground and perpendicular to the cylinder axis 120a, and can rotate. The central portion of the camshaft 136 may be positioned on the cylinder axis 120a and may be biased in the direction of the first roller follower 132a or the second roller follower 132b with respect to the center of the cam 136 . Preferably, the distance between the center of the camshaft 136 and the center of the first roller follower 132a: the distance between the center of the camshaft 136 and the center of the second roller follower 132b is 1: 1.3 to 2.4 And most preferably 1: 1.5. Each of the cams of the first, second, and third driving units shares the camshaft, and the angular difference between the center line of the cam passing the center of the camshaft and the cylinder axis is 120 Deg.] Relative to the camshaft. Therefore, the displacements of the respective cams 135 may be different on the basis of the stop state at a specific point in time.

When the cam 135 rotates, the pair of roller followers 132a and 132b, which are grounded on the outer surface of the cam 135, reciprocate on the cylinder axis 120a, The reciprocating motion of the followers 132a and 132b, the guide pistons 131a and 131b and the plunger 122 can be switched. Since the first roller follower 131a and the second roller follower 131b are fixed by the hanger rod 134, the plunger 122 can be moved in any direction of reciprocation according to the rotation of the cam 135 .

Hereinafter, the use and function of the pulsatile metering pump according to the present invention will be described with reference to FIGS. 4 and 5. FIG.

4 is a graph showing the change in position of the plunger 122 with respect to the rotation of the cam 135 on the vertical axis and the rotation angle of the cam 135 on the horizontal axis. 4A is a graph showing changes in the positional change, speed, and acceleration of the plunger 122 as the cam 135 of the first driver 100 rotates. 3 driving unit 300 according to the rotation angle of each cam of the plunger 122 according to the first embodiment of the present invention.

Referring to FIG. 4A, the movement of the cam 135 is largely divided into a rising region where the displacement of the plunger 122 increases (i.e.,? = 0 to 180 占 and a cam (I.e.,? = 180 to 360) in which the displacement of the plunger 122 decreases as the rotation angle of the plunger 122 increases. When the rising region where the displacement of the plunger 122 increases (i.e.,? = 0 to 180 占) is subdivided, the stop region 1 in which the displacement of the plunger 122 does not change as the rotation angle of the cam 135 increases (θ = 55 to 125 °), which is increased at a constant speed, such as θ = 0 to 5 °, an increasing region 1 (ie, θ = 5 to 55 °) (I.e., θ = 125 to 175 °) and a non-changing stop region 2 (ie, θ = 175 to 180 °).

That is, in the rising region, as the cam 135 rotates, the plunger 122 moves along the cylinder wall 121 in the direction of the head portion 110 and the displacement rises. In the falling region, the cam 135 rotates The plunger 122 moves in the direction of the moving part 130 along the cylinder wall 121 to reduce the displacement. The rising region and the falling region may have a line symmetric structure. The rising region includes an acceleration portion (i.e.,? = 5 to 55 占 where the displacement of the plunger 122 accelerates at an accelerating speed, a constant velocity portion (i.e.? = 55 to 125 占 at which the displacement varies uniformly) And a decelerating portion in which the displacement changes slowly (i.e.,? = 125 to 175 degrees). In order to smoothly operate the suction check ball 112a and the discharge check ball 114a, the stop zone 1 (that is, θ = 0 to 5 °) and the stop zone 2 (that is, θ = 175 to 180 °) .

Referring to FIG. 4B, the principle of motion of the first driver illustrated in FIG. 4A is applied to the second and third drivers with a phase difference of 120 degrees. The sum of the displacement change per unit revolution (i.e., DELTA h1 / DELTA [theta]) of the acceleration portion and the displacement change per unit revolution (i.e., DELTA h2 / DELTA h / DELTA &thetas;). That is, the relation of? H1 +? H2 =? H can be established at all angular positions belonging to the region (I) of FIG. 4B.

5 is a view schematically illustrating the discharging and sucking process of the pulsating flow rate measuring pump according to the present invention. More specifically, FIG. 5A is a view showing a still state when the rotation angle of the cam 135 is 0 ° in the graph of FIG. 4, and FIG. 5B is a diagram showing the rotation angle of the cam 135 in the graph of FIG. 180 ". < / RTI >

4 and 5, the displacement of the plunger 122, which is slidable horizontally with respect to the cylinder axis 120a, increases as the cam 135 rotates from 0 ° to 180 °, that is, So that pressure can be applied to the fluid existing in the pressurizing chamber 116. When the pressure in the fluid in the pressurizing chamber 116 is generated as described above, the discharge check ball 114a blocking the discharge check ball seat 114b rises and the fluid can be discharged to the outside of the head unit 110 through the discharge port . At the same time, the suction check ball 112a is brought into close contact with the suction check ball seat 112b by the pressure of the fluid, so that the fluid can not be sucked into the head portion through the suction port 112.

On the contrary, when the cam 135 rotates in the direction of 360 ° from 180 °, the displacement of the plunger 122 decreases, that is, the sliding movement is performed in the opposite direction of the head portion, . As the pressure in the pressurizing chamber 116 decreases, the suction check ball 112a blocking the suction check ball seat 112b rises and the fluid flows into the head through the suction port and the pressure chamber 116 and the moving pipe 113 ). At the same time, the discharge check ball 114a is brought into close contact with the discharge check ball seat 114b by the reduced pressure, so that the fluid can be prevented from being discharged through the discharge hole 114. [

In the above-described suction / discharge process, the first to third driving units are simultaneously operated with a phase difference of 120 °. 4B, the plunger 135a of the first driving part 100 is moving at an equal speed in the direction of the head part 110, and the plunger 135a of the second driving part 200 And the plunger 135c of the third driving unit 300 moves in the direction of the head unit 110 in a constant decelerating manner. In this manner, the plunger 135 of one of the driving portions exhibits a constant velocity motion and the plunger of the remaining two driving portions exhibits an equivalent velocity or an equal decelerating motion at every rotation angle of the cam.

4B, the plunger 135a of the first driving part and the plunger 135b of the third driving part are in the discharging step, and the combined discharge amount at this time is represented by DELTA h1 + DELTA h2 . 4B, only the plunger 135a of the first driving portion is in the discharging step, and the discharging amount? Q at this time can be expressed by? H. Since the outer surface of the cam 135 is designed so that? H1 +? H2 =? H is established as described above, the discharge amount in the section I and the discharge amount in the section II are the same, The same discharge amount can be maintained. Likewise, the intake amount can also be kept the same throughout the whole section.

In this way, the pulsation of the pulsating pump of the present invention may not be generated because the suction amount and the discharge amount are constant at any interval.

The preferred embodiments of the present invention have been described in detail with reference to the drawings. It will be understood by those of ordinary skill in the art that various changes in form and details may be made therein without departing from the spirit and scope of the present invention as defined by the appended claims.

Accordingly, the scope of the present invention is defined by the appended claims rather than the foregoing detailed description, and all changes or modifications derived from the meaning, range, and equivalence of the claims are to be construed as being included within the scope of the present invention do.

100: first driving part 110:
111: suction pipe 112a: suction check ball
112b: Suction check ball seat 112: Suction port
113: moving pipe 114a: discharge check ball
114b: Discharge check ball seat 114: Discharge port
115: discharge pipe 116: pressure chamber
120: cylinder part 121: cylinder wall
122: plunger 130:
131a: first guide piston 131b: second guide piston
132a: first roller follower 132b: second roller follower
133a: first roller follower shaft 133b: second roller follower shaft
134: Hanger rod 134a: Hanger pipe
134b: hanger stand 134c: spring
134d: Nut 134e: Connection pin
135: cam 135a: first drive cam
135b: second driving portion cam 135c: third driving portion cam
135d: Cam rotation center
136: camshaft 120a: cylinder shaft
137: motor connection part 138: camshaft bearing
200: second driving part 300: third driving part

Claims (3)

(i) a head portion including a suction port formed at an upper / lower end thereof, a discharge port, and a pressure chamber connecting the suction port and the discharge port;
(ii) a cylinder portion connected to the head portion, the plunger slidingly moving in the axial direction of the cylinder; And
(iii) a first guide piston having one end connected to the plunger and the other end connected to the first roller follower; A second guide piston connected to the first guide piston by a hanger rod and reciprocating in a cylinder axial direction integrally with the first guide piston; A second roller follower connected to one end of the second guide piston in a first guide piston direction; And a cam fixed to the camshaft, the camshaft being perpendicular to the axial direction of the cylinder, the camshaft being in contact with the first roller follower and the second roller follower,
A first driving unit including a first driving unit,
And a second driving unit and a third driving unit, each of which includes the same configuration of the first driving unit and is positioned horizontally with respect to the first driving unit,
The cams of the first, second, and third driving units share a camshaft, and the angle difference between the center line of the cam passing through the center of the camshaft and the cylinder axis is θ Pulsating metering pump fixed to a camshaft so as to be 120 DEG with respect to each other,
(? H1) of the plunger per unit rotation of the cam and a decelerating portion (? = H1) at which the displacement of the plunger decelerates at an acceleration portion (? = 5 to 55 占 where the displacement of the plunger accelerates, 125 to 175 deg.), The sum of displacement changes (DELTA h2) of the plungers per unit rotation of the cam is equal to or smaller than the sum of the displacements of the plungers per unit rotation of the cam Wherein the outer surface of the cam is designed to be always equal to the displacement change? H.
2. The pulsating pump according to claim 1, wherein the outer surface of the cam is designed so that an axis distance between the axis of the first roller follower and the axis of the second roller follower is always constant.
2. The image forming apparatus according to claim 1, wherein the distance between the center of the camshaft and the center of the first roller follower: the distance between the center of the camshaft and the center of the second roller follower is 1: 1.3 to 2.4. Pulsatile dosing pump.

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