CN105443347A - High-pressure pump improved structure - Google Patents
High-pressure pump improved structure Download PDFInfo
- Publication number
- CN105443347A CN105443347A CN201511016478.4A CN201511016478A CN105443347A CN 105443347 A CN105443347 A CN 105443347A CN 201511016478 A CN201511016478 A CN 201511016478A CN 105443347 A CN105443347 A CN 105443347A
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- CN
- China
- Prior art keywords
- cam gear
- service pump
- pressure service
- node method
- modified node
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- 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
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
-
- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms
- F16H53/02—Single-track cams for single-revolution cycles; Camshafts with such cams
- F16H53/025—Single-track cams for single-revolution cycles; Camshafts with such cams characterised by their construction, e.g. assembling or manufacturing features
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Reciprocating Pumps (AREA)
Abstract
The invention relates to a high-pressure pump improved structure which comprises a transmission mechanism connected with a motor, wherein a power output end of the transmission mechanism is connected with a cam gear; a power output end of the cam gear is fit with a double-plunger parallel system; a high-low curved surface is arranged at one end, fit with the double-plunger parallel system, of the cam gear; and a connection line between the highest point and the lowest point of the curved surface is intersected with a central shaft of the cam gear. According to the high-pressure pump improved structure, the curved surface of the cam gear is fit with the double-plunger parallel system, so that a 180-degree phase difference is formed between plungers by a fluid in a high-pressure pump, fluid pulse is weakened, the stability of the flow in the whole process is guaranteed, and the problem that internal pressure of the high-pressure pump fluctuates greatly due to the fluid pulse is alleviated.
Description
Technical field
The present invention relates to pump field, particularly, relate to a kind of high-pressure service pump modified node method.
Background technique
High-pressure service pump is a kind of equipment providing high voltage power.High-pressure service pump is generally reciprocating pump, and wherein motor is through driving mechanism driving cam, cam again by power transmission to piston column, piston column to be arranged in cylinder body from entrance pumping fluid and to discharge from outlet under stress.
High-pressure service pump in use, because the end face of cam gear is plane structure, is subject to the impact of fluid pulse, causes pressure surge very large.
Summary of the invention
Technical problem to be solved by this invention is to provide a kind of high-pressure service pump modified node method of almost no pulse fluctuation in fluid passage, to overcome the large problem of pressure surge that existing high-pressure service pump causes because of fluid pulse.
The present invention's adopted technological scheme that solves the problem is: high-pressure service pump modified node method, comprise the driving mechanism be connected with motor, the clutch end of driving mechanism is connected with cam gear, the clutch end of cam gear is equipped with double-plunger parallel system, one end end face that described cam gear coordinates with double-plunger parallel system is set to one high and one low curved surface, and the line of the highs and lows of curved surface is crossing with the central shaft of cam gear.
Existing high-pressure service pump normally adopts single plunger mechanism, the cam gear coordinated with single plunger is plane structure, such structure in use can cause producing fluid pulse in pump, and then it is large to cause pump internal pressure to fluctuate, and makes the flow meter pressure that high-pressure service pump can not provide constant.
One high and one low curved surface of the present invention specifically refers to the radial direction in cam gear as symmetry axis, cam gear is low in the height side, height side of symmetry axis both sides, and the height of described cam gear specifically refers to one end that in cam, device coordinates with double-plunger parallel system distance to the other end; Namely be initial baseline with the radius at cam gear peak place, counterclockwise or turn clockwise after 180 ° and arrive in the process of the radius at cam gear minimum point place, the height of cam gear reduces gradually; Specifically refer to highs and lows circular cross-section on cam gear same radial direction in crossing with the central shaft of cam gear of the line of the highs and lows of described curved surface is that symmetry center is symmetrical arranged with the center of circle; Described motor preferred high accuracy stepper motor, has high-resolution, can be responsive control change in flow, stability and reproducible.
Curved surface set by cam gear of the present invention coordinates with double-plunger parallel system, make high-pressure service pump inner fluid between injecting, form the phase difference of 180 °, weaken fluid pulse, guarantee the steady of whole process flow, slow down the pump internal pressure caused because of fluid pulse and to fluctuate large problem.
Further, one end of coordinating with double-plunger parallel system of cam gear to the height of the other end from low side to high-end at the uniform velocity variation tendency.
The increasing amount of cam gear height can convert as the bolus amount of unit time, and the at the uniform velocity change of cam gear height ensures that cam gear provides constant flow and power when uniform rotation.
Further, cam gear is identical with the center of circle height value sum of 2 symmetrically arbitrarily.
Namely identical to the height sum of cam gear the other end end face with center of circle any two points symmetrically on cam gear curved surface, cam gear the other end end face specifically refers to one end end face relative with curved surface, the described center of circle specifically refers to the center of cam gear radial cross section, it is on the central shaft of cam gear, describedly specifically refer to 2 points differing 180 ° at cam gear upper angle with the center of circle symmetrically 2, curved surface and the double-plunger parallel system of structure like this coordinate can guarantee that the liquid volume summation that both sides take in whole bolus infusion processes is equal, and then ensure that whole process flow steadily and pressure steady.
Further, the operational formula of cam gear height value is:
Wherein, X is the radian value of angle θ, and angle θ is be initial baseline with the radius at cam gear peak place, and the angle be rotated counterclockwise, 0 °≤θ≤360 °, y is the height of cam gear.
According to two of center of circle symmetry points (on cam and angle differ 2 points of the 180 °) principle that height overall sum remains unchanged, be illustrated in fig. 5 shown below:
I.e. h1+h1 ' ≈ h3 '+h3;
According to mentioned above principle, in conjunction with cam gear actual processing, be met the data of the cam gear height of mentioned above principle as shown in Figure 6:
Again by curve, obtain the curvilinear equation of cam gear actual height:
Wherein, each parameter value is as follows:
Intercept-0.10268
B10.56981
B20.80375
B3-0.1425
Namely total formula is:
。
Further, the operational formula of cam gear height value is:
Wherein, X is the radian value of angle θ, and angle θ is be initial baseline with the radius at cam gear peak place, and the angle be rotated counterclockwise, 0 °≤θ≤360 °, y is the height of cam gear, and π gets 3.1415926.
Concrete thrust process is the same, adopts Sine-Fitting, obtains the curvilinear equation be similar to:
Wherein, each parameter value is as follows:
y03.00099
xc2.02407
w3.24656
A3.30592
Namely total formula is:
。
Further, driving mechanism is planetary gear mechanism.
The power input output of planetary gear mechanism are concentric, have vibration little, without transmission harmonic wave, and noise free, non-lubricating advantage.
Further, planetary gear mechanism comprises 1 gearwheel, gearwheel is evenly provided with 3 small gears, is provided with pto＝power take-off between 3 small gears.
Further, double-plunger parallel system comprises 2 plungers cooperatively interacted.
Further, between 2 plungers at a distance of 3/5 cam gear circumference.
The real data derived by above-mentioned formula can obtain and be similar to 3/5 apart between 2 plungers.
Further, plunger sets gradually main chamber, secondary chamber away from one end of cam gear, and described main chamber, secondary chamber adopt seal ring sealing.
The present invention, by arranging secondary chamber, realizes secondary seal, ensure that seal ring, plunger rod be difficult to wearing and tearing, without leakage, do not fear high salt mobile phase.
High-pressure service pump of the present invention from the pressure data of actual application as shown in Figure 4, as shown in Figure 4, high-pressure service pump of the present invention pressure surge in running is little, flowed fluctuation is ± 0.025ml/min, pressure surge is ± 1.5%, the abscissa of Fig. 4 is angle θ, and y coordinate is the trend along with the change pressure of angle θ changes.
To sum up, the invention has the beneficial effects as follows:
1, the curved surface set by cam gear of the present invention coordinates with double-plunger parallel system, make high-pressure service pump inner fluid between injecting, form the phase difference of 180 °, weaken fluid pulse, guarantee the steady of whole process flow, my problem slowing down that the pump internal pressure that causes because of fluid pulse fluctuates large.
2, the present invention is by arranging planetary gear mechanism, reduces the vibration of high-pressure service pump, reduces noise.
3, the present invention realizes secondary seal by arranging secondary chamber, avoids the problem that seal ring, plunger rod wear and tear.
Accompanying drawing explanation
Fig. 1 is the structural representation of high-pressure service pump modified node method;
Fig. 2 is the structural representation that plunger coordinates with cam gear;
Fig. 3 is planetary gear mechanism;
Pressue-graph when Fig. 4 is the work of high-pressure service pump modified node method;
Fig. 5 is that 2 height overall sums of cam gear center of circle symmetry remain unchanged the schematic diagram of principle;
Fig. 6 is the datagram of cam gear actual height.
Mark and corresponding component title in accompanying drawing:
1-motor; 2-driving mechanism; 3-cam gear; 4-plunger; 5-secondary chamber; 6-main chamber; 7-gearwheel; 8-small gear; 9-pto＝power take-off.
Embodiment
Below in conjunction with embodiment and accompanying drawing, to the detailed description further of invention do, but embodiments of the present invention are not limited thereto.
Embodiment 1:
As shown in Figure 1 and Figure 2, high-pressure service pump modified node method, comprise the driving mechanism 2 be connected with motor 1, the clutch end of driving mechanism 2 is connected with cam gear 3, the clutch end of cam gear 3 is equipped with double-plunger parallel system, one end end face that described cam gear 3 coordinates with double-plunger parallel system is set to one high and one low curved surface, and the line of the highs and lows of curved surface is crossing with the central shaft of cam gear 3.
Embodiment 2:
As shown in Figure 1 and Figure 2, the present embodiment based on embodiment 1, one end that described cam gear 3 coordinates with double-plunger parallel system to the height of the other end from low side to high-end at the uniform velocity variation tendency.
Embodiment 3:
As shown in Figure 1 and Figure 2, the present embodiment is based on embodiment 1, and described cam gear 3 is identical with the center of circle height value sum of 2 symmetrically arbitrarily.
Embodiment 4:
As shown in Figure 1 and Figure 2, the present embodiment is based on embodiment 2 or embodiment 3, and the operational formula of described cam gear 3 height value is:
Wherein, X is the radian value of angle θ, and angle θ is be initial baseline with the radius at cam gear 3 peak place, and the angle be rotated counterclockwise, 0 °≤θ≤360 °, y is the height of cam gear 3.
Embodiment 5:
As shown in Figure 1 and Figure 2, the present embodiment is based on embodiment 2 or embodiment 3, and the operational formula of described cam gear 3 height value is:
Wherein, X is the radian value of angle θ, and angle θ is be initial baseline with the radius at cam gear 3 peak place, and the angle be rotated counterclockwise, 0 °≤θ≤360 °, y is the height of cam gear 3, and π gets 3.1415926.
Embodiment 6:
As shown in Figure 1 to Figure 3, described driving mechanism 2 is planetary gear mechanism; Described planetary gear mechanism comprises 1 gearwheel 7, gearwheel 7 is evenly provided with between 3 small gears, 8,3 small gears 8 and is provided with pto＝power take-off 9.
Embodiment 7:
As shown in Figure 1 and Figure 2, the present embodiment is based on embodiment 1, and described double-plunger parallel system comprises 2 plungers cooperatively interacted 4; At a distance of cam gear 3 circumference of 3/5 between described 2 plungers 4; Described plunger 4 sets gradually main chamber 6, secondary chamber 5 away from one end of cam gear 3, and described main chamber 6, secondary chamber 5 adopt seal ring to seal.
Pressure testing results of the present invention as shown in Figure 4.
Working principle of the present invention: power enters driving mechanism 2 from motor 1, further to cam gear 3, now, the operative end surface of cam gear 3 and motor 1, driving mechanism 2 axis are vertical.
Further, 2 plungers cooperatively interacted 4 of phase 180 ° move reciprocatingly with the operative end surface of cam gear 3, and plunger 4 does relatively reciprocating motion with cylinder body, and liquid is flowed out to outlet pulsation by import.
Further, the change of the curved surface of the operative end surface of cam gear 3, the fluctuation reaching pulsating fluid levels off to nothing.
As mentioned above, the present invention can be realized preferably.
Claims (10)
1. high-pressure service pump modified node method, it is characterized in that, comprise the driving mechanism (2) be connected with motor (1), the clutch end of driving mechanism (2) is connected with cam gear (3), the clutch end of cam gear (3) is equipped with double-plunger parallel system, one end end face that described cam gear (3) coordinates with double-plunger parallel system is set to one high and one low curved surface, and the line of the highs and lows of curved surface is crossing with the central shaft of cam gear (3).
2. high-pressure service pump modified node method according to claim 1, is characterized in that, one end that described cam gear (3) coordinates with double-plunger parallel system to the height of the other end from low side to high-end at the uniform velocity variation tendency.
3. high-pressure service pump modified node method according to claim 1, is characterized in that, described cam gear (3) is identical with the center of circle height value sum of 2 symmetrically arbitrarily.
4. high-pressure service pump modified node method according to claim 1, is characterized in that, the operational formula of described cam gear (3) height value is:
Wherein, X is the radian value of angle θ, and angle θ is be initial baseline with the radius at cam gear (3) peak place, and the angle be rotated counterclockwise, 0 °≤θ≤360 °, y is the height of cam gear (3).
5. high-pressure service pump modified node method according to claim 1, is characterized in that, the operational formula of described cam gear (3) height value is:
Wherein, X is the radian value of angle θ, and angle θ is be initial baseline with the radius at cam gear (3) peak place, and the angle be rotated counterclockwise, 0 °≤θ≤360 °, y is the height of cam gear (3), and π gets 3.1415926.
6. high-pressure service pump modified node method according to claim 1, is characterized in that, described driving mechanism (2) is planetary gear mechanism.
7. high-pressure service pump modified node method according to claim 6, it is characterized in that, described planetary gear mechanism comprises 1 gearwheel (7), gearwheel (7) is evenly provided with 3 small gears (8), is provided with pto＝power take-off (9) between 3 small gears (8).
8. high-pressure service pump modified node method according to claim 1, is characterized in that, described double-plunger parallel system comprises 2 plungers cooperatively interacted (4).
9. high-pressure service pump modified node method according to claim 8, is characterized in that, at a distance of cam gear (3) circumference of 3/5 between 2 plungers (4).
10. high-pressure service pump modified node method according to claim 8, is characterized in that, described plunger (4) sets gradually main chamber (6), secondary chamber (5) away from one end of cam gear (3), and described main chamber (6), secondary chamber (5) adopt seal ring sealing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201511016478.4A CN105443347B (en) | 2015-12-31 | 2015-12-31 | High-pressure pump improved structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201511016478.4A CN105443347B (en) | 2015-12-31 | 2015-12-31 | High-pressure pump improved structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105443347A true CN105443347A (en) | 2016-03-30 |
| CN105443347B CN105443347B (en) | 2017-12-01 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201511016478.4A Expired - Fee Related CN105443347B (en) | 2015-12-31 | 2015-12-31 | High-pressure pump improved structure |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201187440Y (en) * | 2008-03-23 | 2009-01-28 | 孙中伟 | Adjustable type electric multi-point grease lubricating pump |
| CN101603516A (en) * | 2009-06-26 | 2009-12-16 | 上海舜宇恒平科学仪器有限公司 | High-pressure constant flow pump for single lobe of liquid chromatograph |
| CN201943909U (en) * | 2010-06-23 | 2011-08-24 | 大连志新科技有限责任公司 | Straight line reciprocating movement mechanism for cam-driven multi-cylinder reciprocating pump |
| CN202001233U (en) * | 2010-06-23 | 2011-10-05 | 大连志新科技有限责任公司 | Cam driving mechanism for multi-cylinder reciprocating pump |
| CN103104432A (en) * | 2013-02-28 | 2013-05-15 | 上海舜宇恒平科学仪器有限公司 | Liquid chromatograph constant flow pump |
| CN205260247U (en) * | 2015-12-31 | 2016-05-25 | 四川奥博生物医学电子有限公司 | High -pressure pump |
-
2015
- 2015-12-31 CN CN201511016478.4A patent/CN105443347B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201187440Y (en) * | 2008-03-23 | 2009-01-28 | 孙中伟 | Adjustable type electric multi-point grease lubricating pump |
| CN101603516A (en) * | 2009-06-26 | 2009-12-16 | 上海舜宇恒平科学仪器有限公司 | High-pressure constant flow pump for single lobe of liquid chromatograph |
| CN201943909U (en) * | 2010-06-23 | 2011-08-24 | 大连志新科技有限责任公司 | Straight line reciprocating movement mechanism for cam-driven multi-cylinder reciprocating pump |
| CN202001233U (en) * | 2010-06-23 | 2011-10-05 | 大连志新科技有限责任公司 | Cam driving mechanism for multi-cylinder reciprocating pump |
| CN103104432A (en) * | 2013-02-28 | 2013-05-15 | 上海舜宇恒平科学仪器有限公司 | Liquid chromatograph constant flow pump |
| CN205260247U (en) * | 2015-12-31 | 2016-05-25 | 四川奥博生物医学电子有限公司 | High -pressure pump |
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| CN105443347B (en) | 2017-12-01 |
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Granted publication date: 20171201 Termination date: 20201231 |