CN116971969A - Bypass type hydraulic diaphragm metering pump - Google Patents
Bypass type hydraulic diaphragm metering pump Download PDFInfo
- Publication number
- CN116971969A CN116971969A CN202311039147.7A CN202311039147A CN116971969A CN 116971969 A CN116971969 A CN 116971969A CN 202311039147 A CN202311039147 A CN 202311039147A CN 116971969 A CN116971969 A CN 116971969A
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- cavity
- bypass
- diaphragm
- oil
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- 239000003921 oil Substances 0.000 claims abstract description 68
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 35
- 230000000903 blocking effect Effects 0.000 claims abstract description 23
- 238000013016 damping Methods 0.000 claims abstract description 22
- 230000000694 effects Effects 0.000 description 10
- 230000009471 action Effects 0.000 description 9
- 238000004891 communication Methods 0.000 description 3
- 238000005086 pumping Methods 0.000 description 3
- 230000003044 adaptive effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000004080 punching Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 239000002253 acid Substances 0.000 description 1
- 239000003513 alkali Substances 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003973 paint Substances 0.000 description 1
- 239000000049 pigment Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000006467 substitution reaction Methods 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
- F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston
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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
- F04B13/00—Pumps specially modified to deliver fixed or variable measured quantities
-
- 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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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
The utility model relates to the technical field of metering pumps, in particular to a bypass type hydraulic diaphragm metering pump, which comprises a diaphragm, wherein one side of the diaphragm is a medium cavity, the other side of the diaphragm is a hydraulic cavity, the hydraulic cavity is communicated with one end of a plunger cavity through a hydraulic channel, and the hydraulic cavity is communicated with an oil storage cavity through an oil control bypass; the other end of the plunger cavity is slidably inserted with a plunger piece, and the external end of the plunger piece is connected with a driving device; the plunger component is linked with a blocking rod which is inserted into or separated from the oil control bypass along with the reciprocating movement of the plunger component so as to enable the oil control bypass to be closed or unblocked; a bypass valve body is arranged in a connecting passage from the hydraulic cavity to the oil control bypass, and a one-way valve allowing hydraulic oil to pass through from the hydraulic cavity to the oil control bypass in one direction and a damping hole always communicating the hydraulic cavity with the oil control bypass are arranged in the bypass valve body; and the flow resistance of the damping hole to hydraulic oil is larger than the deformation resistance of the diaphragm. The bypass type hydraulic diaphragm metering pump can be used for conveying media more efficiently under the working condition of large inlet negative pressure.
Description
Technical Field
The utility model relates to the technical field of metering pumps, in particular to a bypass type hydraulic diaphragm metering pump.
Background
A bypass type hydraulic diaphragm metering pump, such as a bypass oil control type metering pump disclosed in Chinese patent publication No. CN205370883U, is a common pump type device and is widely applied to liquid metering, conveying and pressurizing in chemical technology, such as conveying of acid and alkali liquor, stirring and conveying of pigment, paint spraying and the like.
When the bypass type hydraulic diaphragm metering pump works, the bypass type hydraulic diaphragm metering pump adopts the working principle of the diaphragm pump, and the diaphragm is enabled to move back and forth through compressed air or hydraulic pressure, so that the metering and the conveying of liquid are realized.
It should be noted that, in actual use, it was found that: when the negative pressure at the inlet of the bypass type hydraulic diaphragm metering pump is large, for example, when the bypass type hydraulic diaphragm metering pump is used for conveying certain mediums with high viscosity, the conveying efficiency is low.
Disclosure of Invention
The utility model aims to overcome the defects of the prior art, and provides a bypass type hydraulic diaphragm metering pump which can be used for conveying media more efficiently under the working condition of large inlet negative pressure.
The technical solution of the utility model is as follows:
a bypass hydraulic diaphragm metering pump comprising:
one side of the diaphragm is a medium cavity for directional medium conveying, the other side of the diaphragm is a hydraulic cavity for hydraulic oil flowing, and the hydraulic cavity is communicated with one end of the plunger cavity through a hydraulic channel and is communicated with an oil storage cavity through an oil control bypass;
the other end of the plunger cavity is slidably inserted with a plunger piece, and the external end of the plunger piece is connected with a driving device for driving the plunger piece to slide back and forth in the plunger cavity;
the plunger piece is linked with a blocking rod which is inserted into or separated from the oil control bypass along with the reciprocating movement of the plunger piece so as to enable the oil control bypass to be closed or unblocked;
a bypass valve body is arranged in a connecting passage from the hydraulic cavity to the oil control bypass, and the bypass valve body is internally provided with:
a one-way valve allowing hydraulic oil to pass from the hydraulic cavity to the oil control bypass in one way, and a damping hole always communicating the hydraulic cavity and the oil control bypass;
and the flow resistance of the damping hole to hydraulic oil is larger than the deformation resistance of the diaphragm.
When the negative pressure of the inlet of the bypass type hydraulic diaphragm metering pump is large, for example, when certain mediums with larger viscosity are conveyed, the problem of low conveying efficiency exists, and the following is found: when the medium with larger viscosity is conveyed, the medium with larger viscosity easily generates larger attraction effect on the diaphragm, so that the amplitude of the movement of the diaphragm is reduced, the variable quantity of the volume in the medium cavity is reduced, the suction capacity of the medium cavity to the medium is reduced, the conveying efficiency of the medium in the bypass type hydraulic diaphragm metering pump is negatively influenced, and the medium cannot be conveyed efficiently and stably.
Therefore, the bypass valve body is arranged in the scheme, and is provided with the one-way valve which allows hydraulic oil to pass from the hydraulic cavity to the oil control bypass in one way and the damping hole which is always communicated with the hydraulic cavity and the oil control bypass, so that the flow resistance of the damping hole to the hydraulic oil is larger than the deformation resistance of the diaphragm; when the plunger piece reciprocates in the plunger cavity, and the hydraulic pressure in the hydraulic cavity is changed, the pumping action on the diaphragm (namely, the action of reducing the pressure in the hydraulic cavity and attracting the diaphragm to the bulge of the hydraulic cavity) can be improved while the pushing action on the diaphragm (namely, the action of increasing the pressure in the hydraulic cavity and pushing the diaphragm to the bulge of the medium cavity) is not influenced, so that the medium with larger viscosity is conveyed in a more adaptive manner, the stability of the movement amplitude of the diaphragm can be better ensured when the medium is conveyed, and the stability of the volume variation in the medium cavity is further improved, so that the conveying efficiency of the medium with larger viscosity is improved.
Further as the preferred scheme, the bypass valve body is including the intercommunication the hydraulic pressure chamber with the flow channel of accuse oil bypass, flow channel is close to the one end of hydraulic pressure chamber is provided with the fender lid, be provided with on the fender lid:
the connecting flow passage is communicated with the hydraulic cavity and the damping hole;
and the one-way valve is arranged in the flow channel and acts on the connecting flow channel.
Further preferably, the one-way valve includes:
the piston piece is arranged at an opening of the connecting flow channel towards one end of the flow channel;
and the elastic piece is arranged between the piston piece and the inner wall of the flow channel so as to drive the piston piece to block the connecting flow channel in the direction from the flow channel to the hydraulic cavity.
Further preferably, the elastic member is a spring.
Further preferably, the blocking cover is detachably mounted in the flow channel.
Further preferably, the bypass valve body is detachably mounted in a connection path from the hydraulic chamber to the oil control bypass.
Further preferably, a first limiting plate for limiting the protrusion amplitude of the diaphragm into the hydraulic cavity is arranged in the hydraulic cavity.
Further preferably, a side surface of the first limiting plate facing the diaphragm is an arc surface.
Further as a preferable scheme, the first limiting plate is provided with: the hydraulic oil passes through the first limiting plate and flows to a plurality of first limiting plate runner holes between the first limiting plate and the diaphragm.
Further as the preferred scheme, the hydraulic cavity is communicated with the oil storage cavity through a pressure relief runner, and a pressure relief valve for relieving pressure of the hydraulic cavity is arranged in the pressure relief runner.
The technical scheme has the main beneficial effects that:
the suitability of the bypass type hydraulic diaphragm metering pump for conveying the medium under the working condition of large inlet negative pressure can be improved, the stability of the movement amplitude of the diaphragm can be better ensured when the metering pump conveys the medium under the working condition, and the stability of the volume variation in the medium cavity is further improved, so that the conveying efficiency of the medium is improved.
Further or more detailed benefits will be described in connection with specific embodiments.
Drawings
The utility model is further described with reference to the accompanying drawings:
fig. 1 is a schematic diagram of the internal structure of a metering pump.
Fig. 2 is a schematic diagram of the internal structure of the metering pump.
Fig. 3 is a schematic top cross-sectional view of a metering pump.
Fig. 4 is a schematic side cross-sectional view of a metering pump.
Fig. 5 is a partially enlarged schematic view of X in fig. 3.
The figure shows: the hydraulic oil control device comprises a diaphragm-1, a medium cavity-2, an inlet-201, an outlet-202, a hydraulic cavity-3, a hydraulic channel-4, a plunger cavity-5, an oil control bypass-6, a first oil duct-601, a second oil duct-602, a first port-6021, a second port-6022, an oil storage cavity-7, a plunger piece-8, a blocking rod-9, a bypass valve body-10, a flow channel-1001, a blocking cover-1002, a connecting runner-1002 a, a damping hole-1002 b, a one-way valve-11, a piston piece-1101, an elastic piece-1102, a first limiting plate-12, a first limiting plate runner hole-1201, a pressure relief runner-13, a pressure relief valve-14, a second limiting plate-15, a second limiting plate runner hole-1501, a runner pipe-16, a mounting hole-17, a worm-18, a worm wheel-19, an eccentric wheel-20 and a connecting rod-21.
Detailed Description
The utility model is illustrated by the following examples in which:
embodiment one:
a bypass hydraulic diaphragm metering pump, as shown in figures 1 and 2, comprises a diaphragm 1 disposed in a cavity within a pump body.
As shown in fig. 1 and 3, one side of the diaphragm 1 is a medium cavity 2 for directional medium delivery, and the other side is a hydraulic cavity 3 for hydraulic oil flow.
As shown in fig. 4, the medium chamber 2 generally has an inlet 201 for medium to enter and an outlet 202 for medium to flow out, and a one-way valve is provided in the inlet 201 to allow medium to flow into the medium chamber 2 from outside only, and a one-way valve is also provided in the outlet 202 to allow medium to flow out from the medium chamber 2 only. The check valve may be of the type referred to hereinafter as check valve 11 or of other check valve structures commonly used in metering pumps.
As shown in fig. 1, a plunger cavity 5 is formed by punching in the pump body, one end of the plunger cavity 5 is communicated with the hydraulic cavity 3 through a hydraulic channel 4, a plunger piece 8 which is matched with the aperture setting of the plunger cavity 5 is slidably inserted into the other end, and a driving device for driving the plunger piece 8 to slide back and forth in the plunger cavity 5 is connected to the external end of the plunger piece 8.
Specifically, in this embodiment, as shown in fig. 1 and fig. 2, the driving device includes a worm 18 in driving connection with a rotation motor, the worm 18 is in meshing connection with a worm wheel 19, an eccentric wheel 20 rotating along with rotation of the worm wheel 19 is fixedly connected to the worm wheel 19, one end of a connecting rod 21 is rotatably sleeved on the periphery of the eccentric wheel 20, and the other end of the connecting rod 21 is rotatably connected to an external end of the plunger member 8.
The worm wheel 19 is driven to rotate through the worm wheel 19, the eccentric wheel 20 can be driven to rotate, one end of the connecting rod 21 swings along with the rotation of the eccentric wheel 20, and then the plunger element 8 is driven to move left and right in the plunger cavity 5 through the connecting rod 21, so that the volume of a part, communicated with the hydraulic cavity 3, in the plunger cavity 5 is changed.
Meanwhile, as shown in fig. 3, the hydraulic chamber 3 is communicated with an oil storage chamber 7 for storing hydraulic oil through an oil control bypass 6, and the oil control bypass 6 in this embodiment includes a first oil passage 601 and a second oil passage 602.
Specifically, as shown in fig. 3, in this embodiment, a mounting hole 17 is provided in the pump body, a flow channel pipe 16 is inserted into the mounting hole 17, two ends of the flow channel pipe 16 are sealed and attached to the inner wall of the mounting hole 17, and a space region for hydraulic oil to flow is left between the middle part of the flow channel pipe 16, a part of the first oil channel 601 in the adaptive position and the inner wall of the mounting hole 17.
At this time, the first oil passage 601 is formed by punching in the pump body, the second oil passage 602 is an internal cavity of the flow passage pipe 16 installed in the pump body installation hole 17, the left end of the second oil passage 602 is communicated with the oil storage chamber 7 through a second port 6022 provided on the flow passage pipe 16, and the right end of the second oil passage 602 is communicated with the first oil passage 601 through a first port 6021 provided on the flow passage pipe 16 and the above-mentioned interval region.
Meanwhile, as shown in fig. 3, a plugging rod 9 is inserted into one end of the runner pipe 16, that is, the end of the runner pipe 16 located at one side of the first port 6021 facing away from the second port 6022, and the plugging rod 9 is linked to the plunger 8 through a connecting rod with one end connected to the plugging rod 9 and the other end connected to the plunger 8, so that the plugging rod 9 can be inserted into or separated from the oil control bypass 6 along with the reciprocating movement of the plunger 8, so that the oil control bypass 6 is closed or unblocked.
In this embodiment, when the plunger 8 moves toward the plunger cavity 5, the blocking rod 9 is inserted into the second oil duct 602, and during the insertion process, the blocking rod 9 blocks the first port 6021, so as to realize the sealing of the oil control bypass 6.
Or when the plunger 8 moves towards the outer direction of the plunger cavity 5, the blocking rod 9 is separated from the second oil duct 602, and in the moving process, the blocking rod 9 is separated from the first port 6021, so that the smoothness of the oil control bypass 6 is realized.
At this time, the principle of operation of the metering pump is as follows:
when the plunger 8 moves toward the plunger cavity 5 and the blocking rod 9 moves along with the plunger and does not block the first port 6021, the volume of the portion of the plunger cavity 5 in communication with the hydraulic cavity 3 is reduced by extrusion, so that hydraulic oil originally contained in the plunger cavity 5 is pushed into the hydraulic cavity 3, the pressure in the hydraulic cavity 3 is increased, the increased pressure portion drives the hydraulic oil to push the diaphragm 1, the diaphragm 1 is driven to deform in a protruding trend toward the medium cavity 2, and part of the hydraulic oil is driven to flow from the oil control bypass 6 to the oil storage cavity 7.
With the continuous movement of the plunger 8, the plugging rod 9 plugs the first port 6021, and the pressure generated subsequently drives hydraulic oil to push and act on the diaphragm 1, so as to drive the diaphragm 1 to bulge towards the medium chamber 2, further, the medium originally stored in the medium chamber 2 flows out from the outlet 202 in a directional manner, and under the action of the check valve, the inlet 201 is closed at the moment.
The plunger 8 is then driven to move towards the outside of the plunger cavity 5, and the blocking rod 9 moves along with the plunger and does not separate from the first port 6021, so that the volume of the portion, which is in communication with the hydraulic cavity 3, in the plunger cavity 5 is enlarged, and the hydraulic oil in the hydraulic cavity 3 is sucked into the plunger cavity 5, so that the pressure in the hydraulic cavity 3 is reduced, the reduced pressure forms a low-pressure suction effect, the suction effect portion acts on the diaphragm 1, the diaphragm 1 is driven to deform in a protruding trend towards the hydraulic cavity 3, the portion acts on the first oil duct 601, and the hydraulic oil in the first oil duct 601 is sucked into the hydraulic cavity 3, but since the blocking rod 9 blocks the first port 6021, most of the suction effect acts on the diaphragm 1 at this time, the deformation amplitude of the diaphragm 1 is increased, the volume in the medium cavity 2 is enlarged, the pressure is reduced, so that the external medium can be sucked into the medium cavity 2 from the inlet 201, and under the action of the check valve, the outlet 202 is closed at this time.
With the continuous movement of the plunger 8, the blocking rod 9 is separated from the first port 6021, and the hydraulic oil in the oil storage cavity 7 can be rapidly supplemented into the hydraulic cavity 3, so that the pressure in the hydraulic cavity 3 is kept stable, and the suction effect on the diaphragm 1 can not be performed any more.
Then, the above-mentioned movement of the plunger element 8 toward the interior of the plunger cavity 5 and the movement of the plunger element 8 toward the exterior of the plunger cavity 5 are sequentially repeated, so that the directional delivery of the medium can be realized.
However, it should be noted that: when the negative pressure of the inlet of the bypass type hydraulic diaphragm metering pump is large, for example, when certain mediums with high viscosity are conveyed, the problem of low conveying efficiency exists, namely when the mediums with high viscosity are conveyed, the mediums with high viscosity easily generate a large attraction effect on the diaphragm 1, so that the movement amplitude of the deformation of the diaphragm 1 towards the hydraulic cavity 3 is reduced, the change amount of the volume in the medium cavity 2 is reduced, the suction capacity of the medium cavity 2 to the medium is reduced, the conveying efficiency of the mediums in the bypass type hydraulic diaphragm metering pump is further negatively influenced, and the mediums cannot be conveyed efficiently and stably.
Based on this, as a main improvement point of the present embodiment: as shown in fig. 3, a bypass valve body 10 is provided in a connection passage of the hydraulic chamber 3 to the oil control bypass 6.
Specifically, as shown in fig. 3, a check valve 11 allowing hydraulic oil to pass from the hydraulic chamber 3 to the oil control bypass 6 in one way and a damping hole 1002b communicating the hydraulic chamber 3 and the oil control bypass 6 all the time are arranged in the bypass valve body 10; the flow resistance of the damping hole 1002b to the hydraulic oil is larger than the deformation resistance of the diaphragm 1, and the deformation resistance can be the force required by the diaphragm 1 to block the deformation of the diaphragm towards the bulge of the hydraulic cavity 3, or can be the force required by the diaphragm 1 to block the deformation of the diaphragm towards the bulge of the hydraulic cavity 3 plus the attractive force of the viscous medium, and the specific size can be set according to the actual situation, and meanwhile, the aperture size and the perforating depth of the damping hole 1002b can be set so as to adapt to change the flow resistance of the damping hole 1002b to the hydraulic oil.
Thus, when the plunger 8 moves toward the plunger cavity 5 as described above, the increased pressure in the hydraulic cavity 3 still causes hydraulic oil to flow out from the hydraulic cavity 3, sequentially flows through the bypass valve body 10 and the oil control bypass 6, and flows to the oil storage cavity 7 until the first port 6021 is blocked by the blocking rod 9, and the subsequently generated pressure drives hydraulic oil to push and act on the diaphragm 1, so that the diaphragm 1 is driven to deform in a protruding trend toward the medium cavity 2. I.e. the pushing action of the diaphragm 1 when the plunger element 8 moves into the plunger cavity 5 is not affected, so that the originally stored medium in the medium cavity 2 can still flow out from the outlet 202 in a directional manner.
Meanwhile, when the plunger 8 moves towards the outside of the plunger cavity 5 and the blocking rod 9 moves along with the plunger and is not separated from the first port 6021, the pressure in the hydraulic cavity 3 is reduced to form a low-pressure pumping effect, and the flow resistance of the damping hole 1002b to hydraulic oil is larger than the deformation resistance of the diaphragm 1, so that the pumping effect is more greatly exerted on the diaphragm 1, the diaphragm 1 can be more stably deformed in a protruding trend towards the hydraulic cavity 3, the deformation amplitude of the diaphragm 1 is ensured, and the internal volume expansion and pressure reduction of the medium cavity 2 can be stably realized to stably suck external medium from the inlet 201.
Moreover, as the plunger 8 continues to move and the blocking rod 9 is disengaged from the first port 6021, the suction effect due to the pressure reduction of the hydraulic chamber 3 can still act on the diaphragm 1 due to the arrangement of the check valve 11 and the damping hole 1002b, driving the diaphragm 1 to bulge toward the hydraulic chamber 3.
Further, as shown in fig. 5, the bypass valve body 10 in this embodiment includes a flow channel 1001 for communicating the hydraulic chamber 3 with the oil control bypass 6, a blocking cover 1002 is disposed at one end of the flow channel 1001 near the hydraulic chamber 3, and a connecting flow channel 1002a and a damping hole 1002b for communicating the flow channel 1001 with the hydraulic chamber 3 are disposed on the blocking cover 1002; and the check valve 11 is placed in the flow passage 1001 and acts on the connecting flow passage 1002a.
In this way, when the size of the damping hole 1002b needs to be changed according to different scenes by arranging the damping hole 1002b on the blocking cover 1002, only the blocking cover 1002 with the different damping holes 1002b needs to be arranged in the flow channel 1001, and the bypass valve body 10 itself does not need to be replaced, and the check valve 11 does not need to be replaced.
Still further, as shown in fig. 5, the check valve 11 in the present embodiment includes a piston member 1101 and an elastic member 1102.
Specifically, piston 1101 is disposed at an opening of connecting flow passage 1002a toward one end of flow passage 1001, and elastic member 1102 is disposed between piston 1101 and the inner wall of flow passage 1001 to urge piston 1101 to block connecting flow passage 1002a in the direction from flow passage 1001 to hydraulic chamber 3. Wherein, the elastic fit of the elastic member 1102 prevents the diaphragm 1 from being set up against the convex resistance of the medium chamber 2, that is, achieves the above-mentioned effect, when the plunger 8 moves toward the interior of the plunger chamber 5 and the blocking rod 9 moves along with the plunger and does not block the first port 6021, under the action of the pressure enhancement of the hydraulic chamber 3, the elastic member 1102 can be deformed by compression before the diaphragm 1 protrudes toward the medium chamber 2 or when it protrudes, so that the piston 1101 is separated from the connecting flow passage 1002a, the flow passage 1001, and the oil control bypass 6, and hydraulic oil can enter the oil storage chamber 7 from the connecting flow passage 1002a.
Further, the elastic member 1102 in this embodiment is preferably a spring with a larger gap, so as to facilitate the flow of hydraulic oil.
Meanwhile, the baffle cover 1002 is preferably detachably installed in the flow channel 1001 by adopting, for example, a screw structure, so that the baffle cover 1002 can be conveniently detached to clean the damping hole 1002b which is easy to be blocked on the baffle cover 1002.
The bypass valve body 10 is also preferably detachably mounted in the connection path between the hydraulic chamber 3 and the oil control bypass 6 by adopting, for example, a screw thread structure, so that the bypass valve body 10 can be conveniently mounted or dismounted according to the transportation of media with different characteristics.
Still further, in order to limit the protrusion width of the diaphragm 1 toward the hydraulic chamber 3 according to the requirement, as shown in fig. 3, in this embodiment, a first limiting plate 12 for limiting the protrusion width of the diaphragm 1 toward the hydraulic chamber 3 may be further disposed in the hydraulic chamber 3, and the protrusion width of the diaphragm 1 toward the hydraulic chamber 3 may be limited by disposing a spacing distance between the first limiting plate 12 and the diaphragm 1.
At this time, the first limiting plate 12 is an arc-shaped surface facing one side of the diaphragm 1, can limit the convex shape of the diaphragm 1, drives the diaphragm 1 to be an arc-shaped bulge, and enables the deformation of the diaphragm 1 to be more stable.
In order to reduce the blocking effect of the first limiting plate 12 on the flow of hydraulic oil, as shown in fig. 3, a plurality of first limiting plate flow passage holes 1201 through which hydraulic oil passes through the first limiting plate 12 and flows between the first limiting plate 12 and the diaphragm 1 may be further provided on the first limiting plate 12. In this embodiment, in the direction from the side of the first limiting plate 12 facing away from the diaphragm 1 to the side of the first limiting plate 12 facing toward the diaphragm 1, the aperture of the flow passage hole 1201 of the first limiting plate is reduced first and then unchanged.
Meanwhile, as shown in fig. 3, a second limiting plate 15 for limiting the protrusion amplitude of the diaphragm 1 into the medium chamber 2 may be arranged in the medium chamber 2.
The second limiting plate 15 is also preferably an arc-shaped surface facing one side of the diaphragm 1, and can limit the convex shape of the diaphragm 1, so as to drive the diaphragm 1 to be an arc-shaped convex, and the deformation of the diaphragm 1 is more stable. And a plurality of second limiting plate runner holes 1501 are formed in the second limiting plate 15 for the medium to pass through the second limiting plate 15 and flow between the second limiting plate 15 and the diaphragm 1.
On the basis of the above, as shown in fig. 4, the hydraulic chamber 3 may be further communicated with the oil storage chamber 7 through a pressure release flow channel 13, and a pressure release valve 14 for releasing pressure of the hydraulic chamber 3 is provided in the pressure release flow channel 13, so that when the pressure in the hydraulic chamber 3 is too high, the pressure release valve 14 can be opened by hydraulic oil under the action of high pressure to keep the pressure release flow channel 13 smooth, and further hydraulic oil in the overpressure part flows from the hydraulic chamber 3 to the oil storage chamber 7 through the pressure release flow channel 13. And the relief valve 14 is preferably a relief valve commonly used in the pump art, and the specific structure of the relief valve 14 will not be described in detail here.
The foregoing description is only of the preferred embodiments of the utility model and is not intended to limit the scope of the utility model. In addition, references to the terms "vertical", "horizontal", "front", "rear", etc., in the embodiments of the present utility model indicate that the apparatus or element in question has been put into practice, based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship in which the product is conventionally put in use, merely for convenience of description and to simplify the description, but do not indicate or imply that the apparatus or element in question must have a particular orientation, be constructed and operated in a particular orientation, and therefore should not be construed as limiting the utility model. It should be further noted that, unless explicitly stated or limited otherwise, terms such as "mounted," "connected," "secured," and the like in the description are to be construed broadly as, for example, "connected," either permanently connected, detachably connected, or integrally connected; either directly or indirectly through intermediaries, or in communication with each other. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances. The utility model will be described in detail below with reference to the drawings in connection with embodiments.
While embodiments of the present utility model have been shown and described, it will be understood by those of ordinary skill in the art that: many changes, modifications, substitutions and variations may be made to the embodiments without departing from the spirit and principles of the utility model, the scope of which is defined by the claims and their equivalents.
Claims (10)
1. A bypass hydraulic diaphragm metering pump comprising:
one side of the diaphragm (1) is a medium cavity (2) for directional medium conveying, the other side of the diaphragm is a hydraulic cavity (3) for hydraulic oil flowing, one end of a plunger cavity (5) is communicated with the hydraulic cavity (3) through a hydraulic channel (4), and an oil storage cavity (7) is communicated with the hydraulic cavity through an oil control bypass (6);
the other end of the plunger cavity (5) is slidably inserted with a plunger element (8), and the external end of the plunger element (8) is connected with a driving device for driving the plunger element to slide back and forth in the plunger cavity (5);
the plunger piece (8) is linked with a blocking rod (9) which is inserted into or separated from the oil control bypass (6) along with the reciprocating movement of the plunger piece (8) so as to enable the oil control bypass (6) to be closed or unblocked;
a bypass valve body (10) is arranged in a connecting passage from the hydraulic cavity (3) to the oil control bypass (6), and the bypass valve body (10) is provided with:
a one-way valve (11) allowing one-way passage of hydraulic oil from the hydraulic chamber (3) to the oil control bypass (6), and a damping hole (1002 b) always communicating the hydraulic chamber (3) with the oil control bypass (6);
and the flow resistance of the damping hole (1002 b) to hydraulic oil is larger than the deformation resistance of the diaphragm (1).
2. A bypass hydraulic diaphragm metering pump according to claim 1, wherein: the bypass valve body (10) is including the intercommunication hydraulic pressure chamber (3) with flow channel (1001) of accuse oil bypass (6), flow channel (1001) are close to one end of hydraulic pressure chamber (3) is provided with fender lid (1002), be provided with on fender lid (1002):
a connecting flow passage (1002 a) and the damping hole (1002 b) that communicate the flow passage (1001) with the hydraulic chamber (3);
and the check valve (11) is disposed in the flow passage (1001) and acts on the connecting flow passage (1002 a).
3. A bypass hydraulic diaphragm metering pump according to claim 2, wherein: the one-way valve (11) comprises:
a piston member (1101) disposed at an opening of the connecting flow path (1002 a) toward one end of the flow path (1001);
-an elastic member (1102) interposed between the piston member (1101) and the inner wall of the flow passage (1001) to urge the piston member (1101) to block the connecting flow passage (1002 a) in the direction from the flow passage (1001) to the hydraulic chamber (3).
4. A bypass hydraulic diaphragm metering pump according to claim 3, wherein: the elastic piece (1102) is a spring.
5. A bypass hydraulic diaphragm metering pump according to claim 3, wherein: the baffle cover (1002) is detachably mounted in the flow channel (1001).
6. A bypass hydraulic diaphragm metering pump according to claim 1, wherein: the bypass valve body (10) is detachably arranged in a connecting passage from the hydraulic cavity (3) to the oil control bypass (6).
7. A bypass hydraulic diaphragm metering pump according to any of claims 1 to 6, characterized in that: a first limiting plate (12) for limiting the protrusion amplitude of the diaphragm (1) into the hydraulic cavity (3) is arranged in the hydraulic cavity (3).
8. The bypass hydraulic diaphragm metering pump of claim 7 wherein: one side surface of the first limiting plate (12) facing the diaphragm (1) is an arc-shaped surface.
9. The bypass hydraulic diaphragm metering pump of claim 7 wherein: the first limiting plate (12) is provided with: the hydraulic oil passes through the first limiting plate (12) and flows to a plurality of first limiting plate runner holes (1201) between the first limiting plate (12) and the diaphragm (1).
10. A bypass hydraulic diaphragm metering pump according to claim 1, wherein: the hydraulic cavity (3) is communicated with the oil storage cavity (7) through a pressure relief flow passage (13), and a pressure relief valve (14) for relieving pressure of the hydraulic cavity (3) is arranged in the pressure relief flow passage (13).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311039147.7A CN116971969A (en) | 2023-08-17 | 2023-08-17 | Bypass type hydraulic diaphragm metering pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311039147.7A CN116971969A (en) | 2023-08-17 | 2023-08-17 | Bypass type hydraulic diaphragm metering pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116971969A true CN116971969A (en) | 2023-10-31 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311039147.7A Pending CN116971969A (en) | 2023-08-17 | 2023-08-17 | Bypass type hydraulic diaphragm metering pump |
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| Country | Link |
|---|---|
| CN (1) | CN116971969A (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2174575Y (en) * | 1992-10-09 | 1994-08-17 | 慈溪市机泵厂 | Bellows metering 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 |
| CN102758754A (en) * | 2012-04-20 | 2012-10-31 | 杭州大潮石化设备有限公司 | Simplified hydraulic end structure of tubular diaphragm metering pump |
| CN205297844U (en) * | 2016-01-07 | 2016-06-08 | 大连劳雷石油化工泵制造有限公司 | Hydraulic pressure bypass guiding valve flow regulator |
| WO2017016642A1 (en) * | 2015-07-30 | 2017-02-02 | Linde Aktiengesellschaft | Device for increasing the pressure of a fluid, having a pressure-limiting valve |
| CN206655791U (en) * | 2017-03-01 | 2017-11-21 | 世通海泰泵业（天津）股份有限公司 | A kind of mechanical pump |
| CN210397049U (en) * | 2019-06-17 | 2020-04-24 | 宝鸡市泵发机械有限公司 | Novel soft piston diaphragm pump |
-
2023
- 2023-08-17 CN CN202311039147.7A patent/CN116971969A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2174575Y (en) * | 1992-10-09 | 1994-08-17 | 慈溪市机泵厂 | Bellows metering 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 |
| CN102758754A (en) * | 2012-04-20 | 2012-10-31 | 杭州大潮石化设备有限公司 | Simplified hydraulic end structure of tubular diaphragm metering pump |
| WO2017016642A1 (en) * | 2015-07-30 | 2017-02-02 | Linde Aktiengesellschaft | Device for increasing the pressure of a fluid, having a pressure-limiting valve |
| CN205297844U (en) * | 2016-01-07 | 2016-06-08 | 大连劳雷石油化工泵制造有限公司 | Hydraulic pressure bypass guiding valve flow regulator |
| CN206655791U (en) * | 2017-03-01 | 2017-11-21 | 世通海泰泵业（天津）股份有限公司 | A kind of mechanical pump |
| CN210397049U (en) * | 2019-06-17 | 2020-04-24 | 宝鸡市泵发机械有限公司 | Novel soft piston diaphragm pump |
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