CN109139434B - Diaphragm non-equipotential deflection deformation control method for diaphragm pump - Google Patents
Diaphragm non-equipotential deflection deformation control method for diaphragm pump Download PDFInfo
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- CN109139434B CN109139434B CN201811252807.9A CN201811252807A CN109139434B CN 109139434 B CN109139434 B CN 109139434B CN 201811252807 A CN201811252807 A CN 201811252807A CN 109139434 B CN109139434 B CN 109139434B
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- 238000000034 method Methods 0.000 title claims abstract description 38
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 118
- 239000003921 oil Substances 0.000 claims description 110
- 230000001502 supplementing effect Effects 0.000 claims description 34
- 230000007246 mechanism Effects 0.000 claims description 27
- 238000007599 discharging Methods 0.000 claims description 15
- 238000007789 sealing Methods 0.000 claims description 9
- 239000013589 supplement Substances 0.000 claims description 4
- 230000009471 action Effects 0.000 claims description 3
- 230000005484 gravity Effects 0.000 claims description 3
- 238000005265 energy consumption Methods 0.000 abstract description 7
- 238000004519 manufacturing process Methods 0.000 description 11
- 230000002159 abnormal effect Effects 0.000 description 8
- 230000005540 biological transmission Effects 0.000 description 7
- 230000000694 effects Effects 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000002035 prolonged effect Effects 0.000 description 5
- 239000012530 fluid Substances 0.000 description 4
- 238000005086 pumping Methods 0.000 description 4
- 239000002002 slurry Substances 0.000 description 3
- 238000001514 detection method Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000010420 art technique Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000012938 design process Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000009347 mechanical transmission Effects 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/06—Pumps having fluid drive
- F04B43/073—Pumps having fluid drive the actuating fluid being controlled by at least one valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
Abstract
The invention relates to a diaphragm non-equipotential deflection deformation control method of a diaphragm pump, which comprises a cylinder body, wherein a diaphragm is arranged in the cylinder body, the whole edge of the diaphragm is positioned on the same plane, and the plane is a middle plane; one side of the diaphragm is a hydraulic oil chamber, and the other side of the diaphragm is a medium chamber; the inner wall of the cylinder body is provided with a limiting section which gradually reduces in diameter from the middle plane to one side of the hydraulic oil chamber; the diaphragm satisfies the following conditions during operation: when the diaphragm is respectively moved from the middle plane to the medium chamber to the normal working end position and the working end position, the stroke of the geometric center position is respectively C and A, and when the diaphragm is respectively moved from the middle plane to the medium chamber to the normal working end position and the working end position, the stroke of the geometric center position is respectively B and D, and then the strokes A, B, C and D satisfy B < D < A < C. The invention can prolong the service life of the diaphragm without affecting the mobility of the medium in the medium chamber, and has high working efficiency, low energy consumption and strong applicability.
Description
Technical Field
The invention belongs to the technical field of pumps in liquid positive displacement machines, and particularly relates to a diaphragm non-equipotential deflection deformation control method of a diaphragm pump.
Background
The diaphragm pump works in such a way that the diaphragm in the cylinder body is driven back and forth, so that the volume of the medium chamber is changed to achieve the purpose of sucking and discharging pumped medium. One side of the diaphragm is a driving part, the other side of the diaphragm is a medium chamber, the driving part is a driving mechanism for driving the diaphragm to move back and forth, the driving mode of the driving mechanism comprises mechanical transmission, hydraulic transmission, pneumatic transmission and the like, and the driving mode is widely applied to hydraulic transmission, namely, the driving mechanism drives hydraulic oil in a hydraulic oil chamber to drive the diaphragm to move back and forth. When the diaphragm is blown to one side of the hydraulic oil, the suction valve group of the medium chamber is opened and sucks the medium due to negative pressure, when the diaphragm is blown to one side of the medium, the suction valve group of the medium chamber is closed due to positive pressure, and meanwhile, the discharge valve group of the medium chamber is opened and discharges the medium due to positive pressure.
The maximum limit deformation quantity of the diaphragm which is driven towards two sides is the same, and the existing diaphragm pump basically adopts the working mode of the diaphragm which is equal to deflection deformation, namely the working deformation quantity of the diaphragm which is driven towards two sides is symmetrical and is basically equal to the maximum limit deformation quantity, and the edge and the root position connected with the inner wall of the cylinder body are most easily damaged to cause the failure of the diaphragm pump because the diaphragm always drives back and forth during working. In order to prolong the service life of the diaphragm, as shown in fig. 1, the diaphragm pump in the original design forms a limiting section 11 with a gradually reduced diameter from the diaphragm 2 to the hydraulic oil chamber 3 side on the inner wall of the cylinder body, and the limiting section 11 corresponds to the limit deformation shape of the diaphragm 2 towards the hydraulic oil chamber 3 side, so that when the diaphragm 2 is driven to the hydraulic oil side, the deformation of the diaphragm 2 is limited by the limiting section 11 to protect the edge of the diaphragm 2, and the diaphragm 2 is not damaged due to abnormal deformation; however, on the side of the medium chamber 4, a similar restriction section 11 is not provided, but in the conventional diaphragm pump, the diaphragm 2 is in an equipotential flexural deformation form, i.e., a=b, and when the diaphragm 2 is inflated to the medium side, the deformation is not controlled because of unrestricted protection, and the diaphragm 2 is damaged due to abnormal deformation. The reason why the similar restriction section is not arranged on the side of the medium chamber 4 is that the medium needs to be sucked and discharged, if the similar restriction section or the restriction plate is arranged on the side of the medium chamber 4, the mobility of the medium in the medium chamber 4 is affected, so that the working efficiency of the pump is reduced, the energy consumption of the pump is increased, the volume of the side part is increased to a certain extent, especially if the pulp medium is pumped, the pumping mobility is seriously affected by the similar restriction section or the restriction plate, even the medium is accumulated between the diaphragm and the side restriction plate, and the pumping medium object (namely, the occasion requiring the diaphragm pump) at the beginning of the development of the diaphragm pump is the slurry medium with poor mobility.
Meanwhile, when the diaphragm pump works, the driving mechanism drives the hydraulic oil in the hydraulic oil chamber 3 to drive the diaphragm 2 to move back and forth, the working deformation amount of the diaphragm 2 moving towards the two sides is also determined by the stroke range and the stroke amount of the driving mechanism, in order to avoid the damage of the diaphragm 2 caused by the over-limit deformation amount due to the abnormal driving of the driving mechanism, the consumption of the hydraulic oil or the unreasonable oil quantity of the oil supplementing and discharging hydraulic oil, the oil supplementing controller 32 and the oil discharging controller 31 are further arranged in the hydraulic oil chamber 3 to further prevent the diaphragm 2 from exceeding the limit deformation amount, the working deformation amount (A, B) of the diaphragm 2 moving towards the two sides in the current design is symmetrical and slightly smaller than the maximum limit deformation amount C, and the distance L=A+B between the oil supplementing controller 32 and the oil discharging controller 31. The technology related to the oil make-up controller 32 and the oil drain controller 31 is also involved in CN102562549A, CN203962353U, but has yet to be further optimized in solving the problem of how to extend the service life of the diaphragm 2.
Disclosure of Invention
Aiming at the defects in the prior art, the technical problem to be solved by the invention is to provide the non-equipotential deflection deformation control method for the diaphragm of the diaphragm pump, so that the problem that the service life of the diaphragm is influenced by easy damage of the diaphragm in the back and forth driving working process is avoided, and the effect of effectively prolonging the service life of the diaphragm while not influencing the mobility of a pumping medium in a medium cavity is achieved.
In order to solve the technical problems, the invention adopts the following technical scheme:
the diaphragm pump diaphragm non-equipotential deflection deformation control method comprises a cylinder body, wherein a diaphragm is arranged in the cylinder body, the edge of the diaphragm is in sealing connection with the inner wall of the cylinder body and is positioned on the same plane, and the plane is a middle plane; one side of the diaphragm is a hydraulic oil chamber, the other side of the diaphragm is a medium chamber, and a suction valve group and a discharge valve group are communicated with the medium chamber; a driving mechanism is arranged on one side of the hydraulic oil chamber away from the diaphragm to drive the hydraulic oil in the hydraulic oil chamber to drive the diaphragm to move back and forth; the inner wall of the cylinder body is provided with a limiting section which gradually reduces from the middle plane to one side of the hydraulic oil chamber;
the diaphragm satisfies the following conditions during operation: when the diaphragm is arranged to bulge from the middle plane to the hydraulic oil chamber to the working limit position, the stroke of the geometric center position of the diaphragm is C; when the diaphragm is arranged to bulge from the middle plane to the hydraulic oil chamber to a normal working starting position, the stroke of the geometric center position of the diaphragm is A; when the diaphragm is moved from the middle plane to the medium chamber to the normal working end position, the stroke of the geometric center position is B, and when the diaphragm is moved from the middle plane to the medium chamber to the working limit position, the stroke of the geometric center position is D, and the strokes A, B, C and D meet the conditions that B is less than D is less than A and less than C.
According to the diaphragm non-equipotential deflection deformation control method of the diaphragm pump, through the corresponding matching of the stroke range and the stroke amount of the driving mechanism and the diaphragm driving stroke, the working deformation amount of the diaphragm driving towards the medium side is smaller than the working deformation amount driving towards the hydraulic oil side, namely B is smaller than A, and the non-equipotential deflection deformation working form of the diaphragm is realized; when the diaphragm is driven to the hydraulic oil side, the deformation of the diaphragm is limited by the limiting section so as to protect the edge of the diaphragm, the diaphragm cannot be damaged due to abnormal deformation, when the diaphragm is driven to the medium side, the root and the edge of the diaphragm cannot generate excessive abnormal deformation because the working deformation of the diaphragm driven to the medium side is relatively smaller because B is smaller than D and A is smaller, and the deflection stress and the tensile stress born by the diaphragm when the diaphragm is driven to the medium chamber to the normal working end position and the working limit position are reduced, so that the diaphragm is effectively protected on the medium side; therefore, the movement deformation of the diaphragm to two sides is limited and protected, and the service life of the diaphragm is effectively prolonged; meanwhile, the medium chamber does not need to be provided with a structure similar to a limiting section, the fluidity of the pumped medium in the medium chamber is not influenced, slurry medium is prevented from accumulating at the root of the diaphragm, the working efficiency of the pump is improved, the energy consumption is reduced, and the diaphragm pump can be widely applied to various occasions and is better applied to pumping slurry medium with poor fluidity.
Further perfecting the technical scheme, the geometric center of the side surface of the diaphragm, which faces the hydraulic oil chamber, is provided with a guide rod, the free end of the guide rod faces the direction away from the diaphragm and is connected with a trigger, and the guide rod is communicated with the hydraulic oil chamber and is provided with an oil discharge controller and an oil supplement controller; in the stroke direction of the trigger, the setting position of the oil supplementing controller corresponds to the position of the trigger when the diaphragm is driven to the normal working starting position towards the hydraulic oil chamber, and the setting position of the oil discharging controller corresponds to the position of the trigger when the diaphragm is driven to the working limiting position towards the medium chamber.
In this way, the setting positions of the oil supplementing controller and the oil discharging controller are designed, so that the diaphragm can not exceed the limit deformation amount when being driven to two sides under any condition, and the deflection amount of the diaphragm on the hydraulic oil side is larger than that on the medium side. If expressed by a mathematical expression, that is, when the diaphragm is moved to the hydraulic oil side to a normal working starting position, the distance from the trigger to the middle plane is X, and the distance from the oil supplementing controller to the middle plane is determined as Y, then y=x; in the stroke direction of the trigger, the oil discharge controller is positioned between the oil supplementing controller and the diaphragm, the distance between the oil supplementing controller and the oil discharge controller is determined to be L, then L=A+D, the stroke is A+B when the diaphragm works normally, and because the L=A+D is used for supplementing the hydraulic oil chamber after the oil supplementing controller monitors that the oil supplementing is needed, the diaphragm deviates from the normal working starting position of the diaphragm at the hydraulic oil side to the medium chamber side after the oil supplementing is finished each time, so the trigger of the oil discharge controller does not trigger the oil supplementing controller and the oil discharge controller when the operation is continued, namely the diaphragm works in a non-equipotential deflection deformation mode, when the diaphragm bulges to the normal working starting position to the hydraulic oil side due to special conditions (such as reduction of the consumption of the hydraulic oil), the trigger triggers the oil supplementing controller to work, the hydraulic oil with the external oil supplementing pressure is timely supplemented into the chamber, the diaphragm can move to the direction away from the central plane of the diaphragm when the oil supplementing is needed when the trigger triggers the oil supplementing controller, the hydraulic oil is possibly continuously moved to the hydraulic oil side, and the diaphragm is prevented from being damaged to the limit position when the oil supplementing speed is matched with the hydraulic oil in the oil discharge controller, and the oil is prevented from being stopped; similarly, when the diaphragm is driven to the medium side to trigger the oil discharge controller (namely, the diaphragm is at the working limit position of the medium side because of L=A+D) due to special conditions (such as excessive oil supplementing and the like), the oil discharge controller works and timely discharges part of hydraulic oil in the hydraulic oil chamber, so that the diaphragm is prevented from being damaged, and the oil discharge is stopped after the trigger returns to the position between the oil supplementing controller and the oil discharge controller; therefore, the non-equipotential deflection deformation of the diaphragm is controlled, and the effect of effectively prolonging the service life of the diaphragm is better ensured.
Further, the method for obtaining the stroke C comprises the following steps: a distance measuring tool is arranged in the medium chamber, a distance measuring target point is the geometric center position of the diaphragm facing one side surface of the medium chamber, when the medium chamber is pressurized to enable the diaphragm to bulge towards the hydraulic oil chamber until the edge of the diaphragm is attached to the limiting section, the distance is detected, the distance from the distance measuring tool to the middle plane is a fixed value, and the value of C can be calculated;
the method for obtaining the stroke A comprises the following steps: the driving mechanism is moved to a working starting position of the driving mechanism far away from the diaphragm, hydraulic oil is filled into the hydraulic oil cavity through an oil filling valve communicated with the hydraulic oil cavity, and the oil filling valve is closed; the hydraulic oil makes the diaphragm move to the side of the medium chamber by a certain amount under the action of gravity, and the value of A is calculated by detecting the distance by a measuring tool;
the method for obtaining the stroke B comprises the following steps: on the basis of the state of obtaining the value A, moving the driving mechanism from a driving mechanism working starting position far away from the diaphragm to a driving mechanism working ending position close to the diaphragm, driving the diaphragm to a normal working ending position by driving hydraulic oil in a hydraulic oil cavity, and detecting the distance by a measuring tool to calculate the value B;
the method for obtaining the travel D comprises the following steps: after A, B and C values are obtained, the volume contained by the diaphragm between the strokes A and B is recorded as V1, and the volume contained by the diaphragm between the strokes C and D is set as V2;
v2 = k x V1, k is a coefficient and k is more than or equal to 1.35, D value can be obtained through the formula, the obtained D value can meet B < D < A and k is more than or equal to 1.35, otherwise, the C value needs to be adjusted.
Therefore, the traditional design and manufacturing mode of matching the stroke range and the stroke amount of the driving mechanism through the given symmetrical positions of the limit deformation amount of the diaphragm is broken, the non-equipotential deformation control distance of the diaphragm is determined through the actual driving operation position of the diaphragm, and the diaphragm is objective and real, so that the service life of the diaphragm is prolonged more easily.
Further, the cylinder body comprises a driving cylinder and a medium cylinder which are buckled with each other, the driving cylinder and the medium cylinder are respectively provided with an annular buckling plane and are in buckling connection with each other through the two annular buckling planes, the edge of the diaphragm is clamped between the two annular buckling planes to realize sealing connection with the inner wall of the cylinder body, and the annular buckling planes are coplanar with the middle plane.
Therefore, the cylinder body is convenient to manufacture and assemble, and the sealing connection with the diaphragm is simple and reliable.
Further, the hydraulic oil chamber and the driving mechanism are arranged in the driving cylinder, the driving mechanism comprises a piston, the piston is slidably connected in a piston channel in the driving cylinder, the piston channel is communicated with the small end of the limiting section, and a space between the piston and the diaphragm is formed into the hydraulic oil chamber; the axial direction of the piston channel is in the same direction with the stroke direction of the geometric center position of the piston channel when the diaphragm is in the inflation, the oil discharge controller and the oil supplementing controller are arranged in one end of the piston channel, which is close to the diaphragm, and the free end of the guide rod extends into the piston channel and enables the movement stroke of the trigger to be also in the piston channel.
In this way, the trigger is connected to the geometric center of the side surface of the diaphragm facing the hydraulic oil chamber, and the stroke direction of the geometric center position of the diaphragm when the diaphragm is actuated is the stroke direction of the trigger; the piston channel is consistent with the driving direction of the diaphragm and is directly connected with the small end of the limiting section, an indirect space is not needed for connecting the piston channel with the small end of the limiting section, the manufacturing and forming process of the inner cavity of the driving cylinder is simpler, the manufacturing cost is reduced, the acting direction of the piston is the same as the back-and-forth driving direction of the diaphragm, the efficiency of the piston acting on the force transmission of hydraulic oil is higher, the fluid energy loss of the hydraulic oil is avoided, and the energy consumption of the pump is reduced. The method does not need an indirect space and adopts a mode of directly connecting a piston channel and a limiting section, so that the length of the limiting section can be properly lengthened, a better protection effect is achieved on the diaphragm, and a larger space is needed to ensure the fluidity and the force transmission efficiency of hydraulic oil in the mode of space connection.
Further, the medium chamber is arranged in the medium cylinder, and the cross section area of the medium chamber is equal in the stroke range from the middle plane to the maximum limit position of the medium chamber when the diaphragm is driven in the stroke direction of the geometric center position of the medium chamber; the suction valve group and the discharge valve group are arranged on the cylinder wall of the medium cylinder.
Therefore, a limit section is not arranged in the medium chamber, and the mobility of the medium in the medium chamber is good; the medium chambers can be all equal-diameter sections, so that the medium cylinder is convenient to manufacture, the medium cylinder is smaller in size, occupies less space and is better in applicability.
Further, the oil discharge controller comprises an oil discharge valve group, and the oil supplementing controller comprises an oil supplementing valve group.
Thus, the implementation of the oil filling and discharging processes is perfected, and the oil discharging controller and the oil filling controller are used for detecting the position of the trigger. When the trigger moves to the setting position of the oil supplementing controller, the oil supplementing controller controls the oil supplementing valve group to be opened and supplement oil, and when the trigger moves to the setting position of the oil discharging controller, the oil discharging controller controls the oil discharging valve group to be opened and discharge oil. There are many prior art techniques for accomplishing this function and they are not described in detail herein.
Compared with the prior art, the invention has the following beneficial effects:
1. the invention provides a working form of diaphragm non-equipotential deflection deformation, designs the relation between the working limit position of the diaphragm to the two sides and the starting and finishing positions of normal working, sets a limiting section to protect the diaphragm from being damaged when reaching the working limit position of the hydraulic oil chamber side, prolongs the service life of the diaphragm, ensures that the diaphragm non-equipotential deflection deformation is controlled under various conditions through a corresponding matched oil supplementing controller and an oil discharging controller, and simultaneously ensures that the diaphragm working limit position at the medium side is far smaller than the deformation limit of the diaphragm so as to ensure the effect of prolonging the service life of the diaphragm better; meanwhile, the medium has good fluidity in the medium cavity, the working efficiency of the pump is high, the energy consumption is low, and the applicability is strong.
2. The cylinder body is simple and convenient to manufacture and assemble, and the manufacturing cost is reduced; the sealing connection between the cylinder body and the diaphragm is simple and reliable, and the service life of the diaphragm is prolonged.
3. The piston channel is directly connected with the limiting section, the acting direction of the piston is the same as the back and forth movement direction of the diaphragm, and compared with a mode of connecting the piston channel with the limiting section by using a larger indirect space, the efficiency of the piston acting on the force transmission of hydraulic oil is higher, the fluid energy loss of the hydraulic oil is small, and the energy consumption of the pump is reduced.
Drawings
FIG. 1-schematic diagram of an allelic deflection deformation control method of a diaphragm pump of original design;
FIG. 2 is a schematic illustration of a method of controlling non-allelic deflection deformation of a diaphragm pump according to an embodiment;
FIG. 3-schematic illustration of the diaphragm of the embodiment actuated to the hydraulic oil side operational limit;
FIG. 4-schematic illustration of the diaphragm of the embodiment actuated to a hydraulic oil side normal service start position;
FIG. 5-schematic illustration of the diaphragm of the embodiment being actuated to a media side normal operation end position;
FIG. 6-schematic illustration of the diaphragm of the embodiment being actuated to a media side operational limit;
fig. 7-an enlarged view of the E position of fig. 2;
FIG. 8 is a schematic diagram of a ranging implementation of a diaphragm pump diaphragm non-allelic flexural deformation control method of an embodiment;
the arrows shown in the drawings indicate the direction of fluid flow through the valve block when the corresponding valve block is in operation, and do not specifically refer to the valve block operating state corresponding to the drawings.
The hydraulic oil measuring device comprises a cylinder body 1, a limiting section 11, a driving cylinder 12, a medium cylinder 13, a piston channel 14, a diaphragm 2, a middle plane 21, a hydraulic oil chamber 3, an oil discharge controller 31, an oil supplementing controller 32, an oil filling valve 33, a medium chamber 4, a suction valve group 41, a discharge valve group 42, a guide rod 5, a trigger 51, a piston 6 and a measuring tool 7.
Detailed Description
The following describes the embodiments of the present invention in further detail with reference to the drawings.
Referring to fig. 2-6, the diaphragm non-equipotential deflection deformation control method of the diaphragm pump comprises a cylinder body 1, wherein a diaphragm 2 is arranged in the cylinder body 1, the edge of the diaphragm 2 is in sealing connection with the inner wall of the cylinder body 1 and is positioned on the same plane, and the plane is a middle plane 21; one side of the diaphragm 2 is a hydraulic oil chamber 3, the other side is a medium chamber 4, and a suction valve group 41 and a discharge valve group 42 are communicated with the medium chamber 4; a driving mechanism is arranged on one side of the hydraulic oil chamber 3 away from the diaphragm 2 to drive hydraulic oil in the hydraulic oil chamber 3 to drive the diaphragm 2 to move back and forth; the inner wall of the cylinder body 1 is provided with a limiting section 11 which gradually reduces from the middle plane 21 to the side of the hydraulic oil chamber 3; the geometric center of the side surface of the diaphragm 2 facing the hydraulic oil chamber 3 is provided with a guide rod 5, the free end of the guide rod 5 faces the direction away from the diaphragm 2 and is connected with a trigger 51, the guide rod is communicated with the hydraulic oil chamber 3 and is provided with an oil discharge controller 31 and an oil supplementing controller 32, and the oil discharge controller 31 is positioned between the oil supplementing controller 32 and the diaphragm 2; the following conditions are also satisfied:
the diaphragm 2 is driven to the working limit position from the middle plane 21 to the hydraulic oil chamber 3, the stroke of the geometric center position is C, and the stroke of the geometric center position of the diaphragm 2 is the stroke of the trigger 51 because the trigger 51 is connected to the geometric center of the side surface of the diaphragm 2 facing the hydraulic oil chamber 3; see fig. 3;
the diaphragm 2 is driven from the middle plane 21 to the hydraulic oil chamber 3 to a normal working starting position, and the stroke of the geometric center position is A and A is less than C; when the diaphragm 2 is driven from the middle plane 21 to the hydraulic oil chamber 3 to a normal working starting position, the distance from the trigger 51 to the middle plane 21 is X; the distance from the oil replenishment controller 32 to the middle plane 21 is Y and y=x, that is, in the stroke direction of the trigger 51, the setting position of the oil replenishment controller 32 corresponds to the position of the trigger 51 when the diaphragm 2 is actuated to the normal operation starting position toward the hydraulic oil chamber 3; see fig. 4;
the diaphragm 2 is driven from the middle plane 21 to the medium chamber 4 to a normal working end position, wherein the stroke of the geometric center position is B and B is less than A; see fig. 5;
the diaphragm 2 is driven from the middle plane 21 to the medium chamber 4 to the working limit position, the stroke of the geometric center position is D, and B is less than D and less than A; in the stroke direction of the trigger 51, the setting position of the oil drain controller 31 corresponds to the position of the trigger 51 when the diaphragm 2 is moved to the working limit position toward the medium chamber 4, that is, the distance between the oil replenishing controller 32 and the oil drain controller 31 is L, l=a+d, see fig. 6;
the cylinder body 1 comprises a driving cylinder 12 and a medium cylinder 13 which are buckled with each other, the driving cylinder 12 and the medium cylinder 13 are respectively provided with an annular buckling plane and are in buckling connection with each other through the two annular buckling planes, the edge of the diaphragm 2 is clamped between the two annular buckling planes to realize sealing connection with the inner wall of the cylinder body 1, and the annular buckling planes are coplanar with the middle plane 21, as shown in fig. 7. In this way, the cylinder body 1 is simple and convenient to manufacture and assemble, and the sealing connection with the diaphragm 2 is simple and reliable. The hydraulic oil chamber 3 and the driving mechanism are arranged in the driving cylinder 12, the driving mechanism comprises a piston 6, the piston 6 is slidably connected in a piston channel 14 in the driving cylinder 12, and the limiting section 11 corresponds to the shape of the diaphragm 2 which is driven to the working limit position towards the hydraulic oil chamber 3; the piston channel 14 communicates with the small end of the restriction section 11 to form a funnel shape, and the space between the piston 6 and the diaphragm 2 is formed as the hydraulic oil chamber 3; the axial direction of the piston channel 14 is the same as the stroke direction of the trigger 51 when the diaphragm 2 is actuated, the oil discharge controller 31 and the oil supplement controller 32 are arranged in one end of the piston channel 14 close to the diaphragm 2, and the free end of the guide rod 5 extends into the piston channel 14 and enables the movement stroke of the trigger 51 to be also in the piston channel 14. In this way, the piston channel 14 is directly connected with the limiting section 11, the acting direction of the piston 6 is the same as the back and forth driving direction of the diaphragm 2, the efficiency of the piston 6 acting on the force transmission of hydraulic oil is high, the fluid energy loss of the hydraulic oil is small, and the energy consumption of the pump is low; the length of the limiting section 11 is longer, and the membrane 2 is better protected. The medium chamber 4 is arranged on the medium cylinder 13, and the cross section area of the whole medium chamber 4 is equal in the stroke direction of the trigger 51; the suction valve block 41 and the discharge valve block 42 are provided in the cylinder wall of the medium cylinder 13. Thus, the mobility of the medium in the medium chamber 4 is good, the manufacture of the medium cylinder 13 is simple and convenient, the volume of the medium cylinder 13 is smaller, the space occupied is less, and the applicability is better. The oil drain controller 31 includes an oil drain valve group, and the oil replenishment controller 32 includes an oil replenishment valve group.
Referring to fig. 8, the present invention also provides a method of obtaining strokes A, B, C and D, which may be used in the design, manufacture or assembly. The method for measuring the stroke C comprises the following steps: a distance measuring tool 7 is arranged on the inner wall of the medium cylinder 13, the distance measuring tool 7 can use a laser distance meter and is arranged on an extension line of the back and forth movement of the geometric center position of the diaphragm 2, a distance measuring target point is the geometric center position of the side surface of the diaphragm 2 towards the medium chamber 4, the piston 6 is moved to a piston working starting position (namely a rear dead center) far away from the diaphragm 2, hydraulic oil is not filled in the hydraulic oil chamber 3, design pressure is applied in the medium chamber 4 to enable the diaphragm 2 to move towards the hydraulic oil chamber 3 until the edge of the diaphragm 2 is attached to the limiting section 11, namely the diaphragm 2 is in a working limit position at the hydraulic oil side, the distance is detected, and the value of C can be calculated according to the fact that the distance from the detection starting point of the distance measuring tool 7 to the middle plane 21 is a fixed value and the fixed value is subtracted according to the detection distance;
the method for measuring the stroke A comprises the following steps: on the basis of obtaining the value C, through the oil filling valve 33 communicated with the hydraulic oil chamber 3, hydraulic oil is filled into the hydraulic oil chamber 3 until an exhaust valve (not shown in the figure) communicated with the hydraulic oil chamber 3 is exhausted, and when the hydraulic oil is exhausted, the oil filling valve 33 is closed, and after the hydraulic oil chamber 3 is filled with hydraulic oil, the oil filling valve 33 and the exhaust valve are closed; the diaphragm 2 deflects towards the medium chamber 4 side under the action of gravity of hydraulic oil, the deflected position is the normal working starting position of the diaphragm 2 at the hydraulic oil side, and the distance is detected by the measuring tool 7, so that the value of A is calculated;
the method for measuring the stroke B comprises the following steps: on the basis of the state of obtaining the value A, the piston 6 is moved from a piston working starting position (rear dead center) far away from the diaphragm 2 to a piston working ending position (front dead center) close to the diaphragm 2, hydraulic oil in the hydraulic oil chamber 3 is driven to drive the diaphragm 2 to move to a normal working ending position, and the distance is detected by the measuring tool 7, so that the value B is calculated;
the method for obtaining the travel D comprises the following steps: after A, B and C values are obtained, the volume of the diaphragm 2 contained between the strokes A and B is recorded as V1 (namely, the volume corresponding to the stroke of the diaphragm 2 from the normal working starting position to the normal working ending position is also the volume corresponding to the stroke of the piston 6 from the rear dead center to the front dead center), and the volume of the diaphragm contained between the strokes C and D is set as V2 (namely, the volume corresponding to the stroke of the diaphragm 2 from the working limit position on the hydraulic oil side to the working limit position on the medium side is obtained);
let v2=kxv1, k be the coefficient and k be more than or equal to 1.35, can get D value, D means a interval value too, can calculate or three-dimensional modeling get, D value that get should meet B < D < A and k be more than or equal to 1.35 condition, otherwise need to adjust B or C value, until D value got can meet B < D < A and k is more than or equal to 1.35. When adjusting the value of C, since the limiting section 11 corresponds to the shape of the diaphragm 2 that is moved toward the hydraulic oil chamber 3 to the working limit position, the value of C is adjusted, and at the same time, the structural shape of the limiting section 11 is adjusted, and when the method is implemented, the limiting section 11 can be adjusted by actually reworking, or the design and manufacturing dimensions of the limiting section 11 can be adjusted in the design process.
In the latter normal use process, the oil filling valve 33 is a normally closed valve, and can be opened for use when the hydraulic oil needs to be replaced or other abnormal conditions need to be met. The distance measuring tool 7 may be attached to or detached from the medium cylinder 13 by attaching or detaching a special window or door to or from the medium cylinder 13 or by attaching or detaching (closing when pressing) the suction valve block 41 and the discharge valve block 42.
Referring to fig. 2-6, according to the diaphragm non-equipotential deflection deformation control method of the diaphragm pump, through the corresponding matching of the stroke amount of the piston 6 in the piston channel 14 and the inflation stroke of the diaphragm 2, the working deformation amount of the diaphragm 2 for inflation to the medium side is smaller than the working deformation amount for inflation to the hydraulic oil side, namely, B < a, and the non-equipotential deflection deformation working form of the diaphragm 2 is realized; when the diaphragm 2 is moved towards the hydraulic oil side, the deformation of the diaphragm 2 is limited by the limiting section 11 to protect the edge of the diaphragm 2, the diaphragm 2 cannot be damaged due to abnormal deformation, when the diaphragm 2 is moved towards the medium side, the root and the edge of the diaphragm 2 cannot generate excessive abnormal deformation because the working deformation of the diaphragm 2 is relatively smaller when B < D < A, and the deflection stress and the tensile stress born by the diaphragm 2 when the diaphragm 2 is moved towards the medium chamber 4 to the working limit position are reduced, so that the diaphragm 2 is effectively protected on the medium side; therefore, the movement deformation of the diaphragm 2 to two sides is limited and protected, and the service life of the diaphragm 2 is effectively prolonged; meanwhile, the setting positions of the oil replenishing controller 32 and the oil discharging controller 31 are designed to ensure that the bulge of the diaphragm 2 towards the two sides does not exceed the limit deformation amount under any condition, wherein the setting position of the oil replenishing controller 32 corresponds to the position of the trigger 51 when the diaphragm 2 bulges towards the hydraulic oil side to the normal working starting position, namely Y=X, and the setting position of the oil discharging controller 31 corresponds to the position of the trigger 51 when the diaphragm 2 bulges towards the medium chamber 4 to the working limit position, namely L=A+D; thus, when the diaphragm 2 flexes to the normal operation starting position, it indicates that the hydraulic oil chamber 3 lacks oil, so that the trigger 51 triggers the oil compensating controller 32 to open the oil compensating valve group and timely supply the hydraulic oil with the external oil compensating pressure to the hydraulic oil chamber 3, at this time, the piston 6 moves to the rear dead center, after oil is supplied, the piston 6 moves to the medium chamber 4 to push the diaphragm 2 to flex in the same direction, in this process, if the leakage amount of the hydraulic oil chamber 3 is smaller than the oil compensating amount, the piston 6 moves to the front dead center, the diaphragm 2 flexes beyond the normal operation ending position, even reaches the operation limiting position of the diaphragm 2 on the medium side to trigger oil discharge, and in the next return stroke, the diaphragm 2 does not reach the normal operation starting position when the piston 6 moves to the rear dead center again, because D < a, and the diaphragm 2 operates in a non-equipotential flexing deformation mode. If the amount of oil leakage from the hydraulic chamber 3 exceeds the amount of oil replenishment (i.e., the amount of oil replenishment is less than the amount of oil leakage) during the flexing of the diaphragm 2 into the medium chamber 4 after oil replenishment, then the diaphragm 2 will not exceed the normal operation end position when the piston 6 is in the front dead center position, and the diaphragm 2 will reach the normal operation start position again to trigger oil replenishment during the return stroke, because B < a, the diaphragm 2 will also operate in a non-allelic flexing deformation mode. The non-equipotential deflection deformation of the diaphragm 2 is controlled, so that the service life of the diaphragm 2 is prolonged and the effect is better ensured.
In practice, the person skilled in the art will know that the stroke C should also be smaller than the stroke of the geometrical centre position of the diaphragm 2 when it is actuated from the median plane 21 to its elastic deformation limit position, determined by the shape of the material itself.
Finally, it is noted that the above embodiments are only for illustrating the technical solution of the present invention and not for limiting the same, and although the present invention has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that modifications and equivalents may be made thereto without departing from the spirit and scope of the technical solution of the present invention, which is intended to be covered by the scope of the claims of the present invention.
Claims (6)
1. The diaphragm pump diaphragm non-equipotential deflection deformation control method comprises a cylinder body, wherein a diaphragm is arranged in the cylinder body, the edge of the diaphragm is in sealing connection with the inner wall of the cylinder body and is positioned on the same plane, and the plane is a middle plane; one side of the diaphragm is a hydraulic oil chamber, the other side of the diaphragm is a medium chamber, and a suction valve group and a discharge valve group are communicated with the medium chamber; a driving mechanism is arranged on one side of the hydraulic oil chamber away from the diaphragm to drive the hydraulic oil in the hydraulic oil chamber to drive the diaphragm to move back and forth; the inner wall of the cylinder body is provided with a limiting section which gradually reduces from the middle plane to one side of the hydraulic oil chamber;
the diaphragm is characterized in that the diaphragm meets the following conditions in operation: when the diaphragm is arranged to bulge from the middle plane to the hydraulic oil chamber to the working limit position, the stroke of the geometric center position of the diaphragm is C; when the diaphragm is arranged to bulge from the middle plane to the hydraulic oil chamber to a normal working starting position, the stroke of the geometric center position of the diaphragm is A; when the diaphragm is driven to a normal working end position from the middle plane to the medium chamber, the stroke of the geometric center position is B, and when the diaphragm is driven to a working limit position from the middle plane to the medium chamber, the stroke of the geometric center position is D, and the strokes A, B, C and D meet the conditions that B is less than D is less than A and less than C;
the method for obtaining the stroke C comprises the following steps: a distance measuring tool is arranged in the medium chamber, a distance measuring target point is the geometric center position of the diaphragm facing one side surface of the medium chamber, when the medium chamber is pressurized to enable the diaphragm to bulge towards the hydraulic oil chamber until the edge of the diaphragm is attached to the limiting section, the distance is detected, the distance from the distance measuring tool to the middle plane is a fixed value, and the value of C can be calculated;
the method for obtaining the stroke A comprises the following steps: the driving mechanism is moved to a working starting position of the driving mechanism far away from the diaphragm, hydraulic oil is filled into the hydraulic oil cavity through an oil filling valve communicated with the hydraulic oil cavity, and the oil filling valve is closed; the hydraulic oil makes the diaphragm move to the side of the medium chamber by a certain amount under the action of gravity, and the value of A is calculated by detecting the distance by a measuring tool;
the method for obtaining the stroke B comprises the following steps: on the basis of the state of obtaining the value A, moving the driving mechanism from a driving mechanism working starting position far away from the diaphragm to a driving mechanism working ending position close to the diaphragm, driving the diaphragm to a normal working ending position by driving hydraulic oil in a hydraulic oil cavity, and detecting the distance by a measuring tool to calculate the value B;
the method for obtaining the travel D comprises the following steps: after A, B and C values are obtained, the volume contained by the diaphragm between the strokes A and B is recorded as V1, and the volume contained by the diaphragm between the strokes C and D is set as V2;
v2 = k x V1, k is a coefficient and k is more than or equal to 1.35, D value can be obtained through the formula, the obtained D value can meet B < D < A and k is more than or equal to 1.35, otherwise, the C value needs to be adjusted.
2. The method for controlling the non-equipotential deflection deformation of a diaphragm pump according to claim 1, wherein: the geometric center of the side surface of the diaphragm, which faces the hydraulic oil chamber, is provided with a guide rod, the free end of the guide rod faces the direction away from the diaphragm and is connected with a trigger, and an oil discharge controller and an oil supplement controller are communicated with the hydraulic oil chamber; in the stroke direction of the trigger, the setting position of the oil supplementing controller corresponds to the position of the trigger when the diaphragm is driven to the normal working starting position towards the hydraulic oil chamber, and the setting position of the oil discharging controller corresponds to the position of the trigger when the diaphragm is driven to the working limiting position towards the medium chamber.
3. The method for controlling the non-equipotential deflection deformation of a diaphragm pump according to claim 2, wherein: the cylinder body comprises a driving cylinder and a medium cylinder which are buckled with each other, the driving cylinder and the medium cylinder are respectively provided with an annular buckling plane and are in buckling connection with each other through the two annular buckling planes, the edge of the diaphragm is clamped between the two annular buckling planes to realize sealing connection with the inner wall of the cylinder body, and the annular buckling planes are coplanar with the middle plane.
4. A method of controlling non-allelic deflection deformation of a diaphragm pump according to claim 3, wherein: the hydraulic oil chamber and the driving mechanism are arranged in the driving cylinder, the driving mechanism comprises a piston, the piston is slidably connected in a piston channel in the driving cylinder, the piston channel is communicated with the small end of the limiting section, and a space between the piston and the diaphragm is formed into the hydraulic oil chamber; the axial direction of the piston channel is in the same direction with the stroke direction of the geometric center position of the piston channel when the diaphragm is in the inflation, the oil discharge controller and the oil supplementing controller are arranged in one end of the piston channel, which is close to the diaphragm, and the free end of the guide rod extends into the piston channel and enables the movement stroke of the trigger to be also in the piston channel.
5. A method of controlling non-allelic deflection deformation of a diaphragm pump according to claim 3, wherein: the medium chamber is arranged in the medium cylinder, and the cross section area of the medium chamber is equal in the stroke range from the middle plane to the maximum limit position of the medium chamber when the diaphragm is driven in the stroke direction of the geometric center position of the medium chamber; the suction valve group and the discharge valve group are arranged on the cylinder wall of the medium cylinder.
6. A method of controlling non-allelic deflection deformation of a diaphragm pump according to claim 3, wherein: the oil discharge controller comprises an oil discharge valve group, and the oil supplementing controller comprises an oil supplementing valve group.
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Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2482246A (en) * | 1947-03-20 | 1949-09-20 | Westinghouse Air Brake Co | Load compensating fluid pressure brake apparatus |
| GB904001A (en) * | 1957-12-03 | 1962-08-22 | Dunlop Rubber Co | Improvements in fluid actuated reciprocating pumps |
| JPH06307341A (en) * | 1993-04-27 | 1994-11-01 | Aisan Ind Co Ltd | Hydraulic type diaphragm pump |
| US6276907B1 (en) * | 1999-08-12 | 2001-08-21 | Wagner Spray Tech Corporation | Hydraulically driven diaphragm pump |
| JP2002138964A (en) * | 2000-11-06 | 2002-05-17 | Oken Ltd | Diaphragm pump |
| CN101263302A (en) * | 2005-07-14 | 2008-09-10 | 霍尼韦尔国际公司 | Asymmetric dual diaphragm pump |
| CN201972872U (en) * | 2010-12-29 | 2011-09-14 | 大庆德美特尔泵业制造有限公司 | Large discharge diaphragm metering pump with oil filling limit and automatic deflation system |
| CN105201794A (en) * | 2015-11-11 | 2015-12-30 | 中国有色(沈阳)泵业有限公司 | Membrane protection system |
| CN107824233A (en) * | 2012-12-21 | 2018-03-23 | 精密公司 | Low elasticity film for microfluidic applications |
-
2018
- 2018-10-25 CN CN201811252807.9A patent/CN109139434B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2482246A (en) * | 1947-03-20 | 1949-09-20 | Westinghouse Air Brake Co | Load compensating fluid pressure brake apparatus |
| GB904001A (en) * | 1957-12-03 | 1962-08-22 | Dunlop Rubber Co | Improvements in fluid actuated reciprocating pumps |
| JPH06307341A (en) * | 1993-04-27 | 1994-11-01 | Aisan Ind Co Ltd | Hydraulic type diaphragm pump |
| US6276907B1 (en) * | 1999-08-12 | 2001-08-21 | Wagner Spray Tech Corporation | Hydraulically driven diaphragm pump |
| JP2002138964A (en) * | 2000-11-06 | 2002-05-17 | Oken Ltd | Diaphragm pump |
| CN101263302A (en) * | 2005-07-14 | 2008-09-10 | 霍尼韦尔国际公司 | Asymmetric dual diaphragm pump |
| CN201972872U (en) * | 2010-12-29 | 2011-09-14 | 大庆德美特尔泵业制造有限公司 | Large discharge diaphragm metering pump with oil filling limit and automatic deflation system |
| CN107824233A (en) * | 2012-12-21 | 2018-03-23 | 精密公司 | Low elasticity film for microfluidic applications |
| CN105201794A (en) * | 2015-11-11 | 2015-12-30 | 中国有色(沈阳)泵业有限公司 | Membrane protection system |
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| CN109139434A (en) | 2019-01-04 |
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