CN113883108A - Continuous flow amplifier and hydraulic press - Google Patents
Continuous flow amplifier and hydraulic press Download PDFInfo
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- CN113883108A CN113883108A CN202111332922.9A CN202111332922A CN113883108A CN 113883108 A CN113883108 A CN 113883108A CN 202111332922 A CN202111332922 A CN 202111332922A CN 113883108 A CN113883108 A CN 113883108A
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- 239000003921 oil Substances 0.000 claims abstract description 329
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 92
- 238000004891 communication Methods 0.000 claims description 11
- 230000003321 amplification Effects 0.000 claims description 5
- 238000003199 nucleic acid amplification method Methods 0.000 claims description 5
- 230000000694 effects Effects 0.000 abstract description 20
- 238000007789 sealing Methods 0.000 abstract description 19
- 230000008901 benefit Effects 0.000 abstract description 17
- 238000004519 manufacturing process Methods 0.000 abstract description 14
- 230000006872 improvement Effects 0.000 abstract description 4
- 238000005265 energy consumption Methods 0.000 abstract description 3
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 238000003825 pressing Methods 0.000 description 12
- 238000000034 method Methods 0.000 description 11
- 230000008569 process Effects 0.000 description 9
- 239000012530 fluid Substances 0.000 description 6
- 238000013461 design Methods 0.000 description 4
- 238000012545 processing Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000001960 triggered effect Effects 0.000 description 2
- 230000003416 augmentation Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
- B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
- F15B11/0426—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling the number of pumps or parallel valves switched on
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a continuous flow amplifier, which comprises a first reversing valve, a first shuttle valve, a flow amplifying cylinder and an oil supply way, wherein the first reversing valve is connected with the first shuttle valve; also discloses a hydraulic cylinder, which comprises a hydraulic cylinder, a pressure oil supply device and the continuous flow amplifier. The invention has the following beneficial effects: the hydraulic system component has the advantages of good sealing performance, low leakage of hydraulic oil, low overall energy loss, effective reduction of energy consumption, capability of improving the sealing performance, capability of selecting hydraulic system components with lower sealing grade and cheaper price, further reduction of manufacturing cost, reduction of failure probability, further improvement of reliability, realization of multiple different working states, capability of adapting to different working states, satisfaction of different use requirements and improvement of applicability and production efficiency. The effect of increasing output flow is realized, and the advantages of high efficiency, good sealing performance, stability, reliability and lower cost are achieved.
Description
Technical Field
The invention relates to the technical field of flow amplifiers, in particular to a continuous flow amplifier and a hydraulic machine.
Background
In the field of hydraulic transmission, in order to improve the working efficiency, an actuating mechanism generally needs to move rapidly when no load or low load exists, such as a rapid return action, a large-stroke low-pressure pressurizing action and the like which are common to large hydraulic machines. In order to meet the large flow demand of a system for a long period of time, the solution adopted in the prior art is to configure a larger displacement or more hydraulic pumps, configure a large number of accumulators, and use a supercharger to pressurize in a reverse direction, which results in high cost of the hydraulic system. The accumulator is filled with pressure oil for a certain time, the pressure oil releasing time of the accumulator is short, the process is uncontrollable, the flow can be controlled only by pressurizing extra throttling measures, and the throttling causes energy loss of the system. The reverse pressurization of the supercharger can only meet the requirement of a small section of low-pressure large-flow hydraulic oil supply due to stroke limitation. Therefore, how to meet the requirements of the system on low cost, continuity and high efficiency has important significance on reducing the cost, increasing the efficiency and saving energy under the working condition of low pressure and large flow.
Chinese patent publication No. CN102588578B discloses a transmission hydraulic control system with flow augmentation, comprising an engine-driven main pump for providing a first supply of hydraulic fluid and an electric motor-driven auxiliary pump; the electric motor driven pump is for providing a second supply of hydraulic fluid. A first check valve disposed in downstream fluid communication with the engine-driven pump and configured to allow a first supply of the hydraulic fluid to flow from the engine-driven pump through the first check valve; a second one-way valve disposed in downstream fluid communication with the electric motor driven pump and configured to allow a second supply of the hydraulic fluid to flow therethrough from the electric motor driven pump. The main pump driven by the engine and the auxiliary pump driven by the electric motor are controlled to work respectively, so that the function of adjusting the flow of the hydraulic system is realized, and the effect of increasing the flow is achieved. Although the effect of increasing the flow rate is achieved by adding the pump and the motor, the additional sealing member is needed after adding the pump and the motor, which results in the increase of the manufacturing cost and the influence of the sealing performance. Therefore, a flow amplifying device with high efficiency, good sealing performance, stability, reliability and low cost is needed in the prior art.
Disclosure of Invention
In order to solve the above technical problems, an object of the present invention is to provide a continuous flow amplifier, which includes a first directional valve, a first shuttle valve, a flow amplifying cylinder, and an oil supply path, and further provide a hydraulic cylinder, which includes a hydraulic cylinder, a pressure oil supply device, and the continuous flow amplifier has the advantages of high efficiency, good sealing performance, stability, reliability, and low cost.
In order to achieve the purpose, the technical scheme adopted by the invention is as follows:
a continuous flow amplifier comprises a first reversing valve, a first shuttle valve, a flow amplifying cylinder and an oil supply oil path, wherein the flow amplifying cylinder comprises a shell, a first driving rod, a second driving rod and a driven piston, a first oil chamber, a second oil chamber, a third oil chamber and a fourth oil chamber are arranged in the shell, the driven piston is fixedly connected with the first driving rod and the second driving rod respectively, the first driving rod, the second driving rod and the driven piston are installed in the shell in a sliding mode, the second oil chamber and the third oil chamber are located on two sides of the driven piston in the sliding direction respectively, the first driving rod extends into the first oil chamber, the second driving rod extends into the fourth oil chamber, the first oil chamber and the fourth oil chamber are communicated with the first reversing valve respectively, the oil supply oil path is communicated with the second oil chamber and the third oil chamber respectively, and the second oil chamber and the third oil chamber are communicated with 2 oil inlets of the first shuttle valve respectively, the first reversing valve is provided with a pressure oil connecting end, and the first shuttle valve is provided with an oil outlet end. By such an arrangement: hydraulic oil flows to the first oil cavity through the pressure oil connecting end and the reversing valve, the hydraulic oil in the first oil cavity pushes the first driving rod to move, the first driving rod drives the driven piston and the second driving rod to move towards the direction far away from the first oil cavity, and the driven piston pushes the hydraulic oil in the third oil cavity to be discharged through the first shuttle valve and the oil outlet end in the moving process. The effect of increasing output flow is realized, and the advantages of high efficiency, good sealing performance, stability, reliability and lower cost are achieved.
Preferably, the first oil chamber and the second oil chamber are respectively communicated with a first shuttle valve, a first valve is arranged between the first oil chamber and the first shuttle valve, a second valve is arranged between the fourth oil chamber and the first shuttle valve, a first one-way valve is arranged between the first oil chamber and the first reversing valve, and a second one-way valve is arranged between the fourth oil chamber and the first reversing valve. By such an arrangement: the hydraulic oil in the first oil cavity and the fourth oil cavity can flow to the first shuttle valve, the flow of the oil outlet end is improved, and the effect of amplifying the flow of the hydraulic oil is achieved.
Preferably, the first valve and the second valve are both hydraulic control valves, a control end of the first valve is communicated with the fourth oil chamber, and a control end of the second valve is communicated with the first oil chamber. By such an arrangement: the function of automatically controlling the opening and closing of the first valve and the second valve according to the pressure oil in the first oil cavity and the second oil cavity is realized.
Preferably, the housing is fixedly provided with a first pressure element and a second pressure element, the first pressure element is located in the first oil cavity and abutted against the first driving rod, the second pressure element is located in the fourth oil cavity and abutted against the second driving rod, and the first pressure element and the second pressure element are respectively connected with the first reversing valve. By such an arrangement: the continuous flow amplifier can automatically and continuously amplify flow, and has the effects of convenience in use and efficiency improvement.
Preferably, the oil supply path is provided with a third one-way valve and a fourth one-way valve, two ends of the third one-way valve are respectively communicated with the oil supply path and the second oil chamber, and two ends of the fourth one-way valve are respectively communicated with the oil supply path and the third oil chamber. By such an arrangement: the stability of the hydraulic oil flow at the oil outlet end is ensured.
Preferably, the first oil chamber is communicated with a first overflow valve, the fourth oil chamber is communicated with a second overflow valve, and the first overflow valve and the second overflow valve are both communicated with the oil supply oil path. By such an arrangement: the hydraulic oil in the first oil cavity and the second oil cavity is prevented from being too high in pressure, and the effects of improving safety and reliability of a hydraulic system are achieved.
Preferably, the first reversing valve is provided with an oil return end, and the oil return end is communicated with the oil supply oil way. By such an arrangement: the oil pressure in the first oil cavity and the oil pressure in the fourth oil cavity are prevented from being equal, so that hydraulic oil cannot push the first driving rod, the second driving rod and the driven piston to move, the oil pressures of the two oil inlets of the first shuttle valve can be prevented from being equal, and the effect of improving the running reliability of equipment is achieved.
The utility model provides a hydraulic press, includes pneumatic cylinder and pressure oil feeding unit, still includes the continuous type flow amplifier among the above-mentioned, the pressure oil link end and the pressure oil feeding unit intercommunication of continuous type flow amplifier, the play oil end and the pneumatic cylinder intercommunication of continuous type flow amplifier. By such an arrangement: the hydraulic cylinder is driven to move quickly, and the effect of improving the working efficiency of the hydraulic machine is achieved.
Preferably, the hydraulic control system further comprises a second reversing valve and a second shuttle valve, the second reversing valve is arranged on a pipeline between the continuous flow amplifier and the pressure oil supply device, the second shuttle valve is arranged on a pipeline between the continuous flow amplifier and the hydraulic cylinder, 2 oil inlets of the second shuttle valve are respectively communicated with the oil outlet end of the continuous flow amplifier and the second reversing valve, the pressure oil supply device is communicated with a hydraulic oil tank, and the second reversing valve is communicated with the hydraulic oil tank. By such an arrangement: the working efficiency is improved, and the method has the advantage of high applicability.
Preferably, the hydraulic control system further comprises a third reversing valve, and the third reversing valve is arranged on a pipeline between the continuous flow amplifier and the hydraulic cylinder. By such an arrangement: the multi-working-state automatic control system has the advantages that various different working states are realized, different working states can be adapted, different use requirements are met, and the effects of improving the applicability and the production efficiency are achieved.
Compared with the prior art, the invention has the beneficial technical effects that:
1. the continuous flow amplifier has no throttling loss and overflow loss when in normal work, the one-way valve and the first shuttle valve can adopt the conical valve core, the one-way valve has the advantage of good sealing property, the leakage of hydraulic oil is reduced, the overall energy loss is small, the advantage of high energy efficiency is achieved, and the energy consumption can be effectively reduced.
2. The flow is automatically and continuously amplified, so that the hydraulic system does not need to be provided with an extra energy accumulator, a pump, a motor and a differential connection flow increasing device, the arrangement structure of the hydraulic system is simpler, the use requirement is met, the manufacturing cost is effectively reduced, the leakage probability of hydraulic oil is reduced, and the effect of improving the sealing property is achieved.
3. Because the hydraulic system does not need to be provided with additional equipment such as an energy accumulator, a pump, a motor and the like, the hydraulic system is favorable for controlling the pressure of hydraulic oil, and the internal pressure of the hydraulic system is smaller, so that the hydraulic system does not need to be designed with an overhigh sealing grade in the design and manufacture process, the hydraulic system is convenient to design and manufacture, and meanwhile, hydraulic system elements with lower sealing grade and cheaper price can be selected, so that the manufacturing cost can be further reduced.
4. The continuous flow amplifier has very high reliability during operation due to the low internal pressure of the hydraulic system. The first pressure element and the second pressure element directly control the switching of the communication state of the first reversing valve, the complexity of the system is effectively reduced, the probability of failure is further reduced, and the reliability is further improved.
5. And the hydraulic machine can be switched into 5 different working states by combining the continuous flow amplifier, the second reversing valve and the third reversing valve. Therefore, various different working states are realized, different working states can be adapted, different use requirements are met, and the effects of improving the applicability and the production efficiency are achieved.
Drawings
Fig. 1 is a schematic structural view of a continuous flow rate amplifier in embodiment 1 of the present invention when a first direction valve supplies pressure oil to a first oil chamber;
fig. 2 is a schematic structural view of a continuous flow rate amplifier in embodiment 1 of the present invention when a first direction changing valve supplies pressure oil to a fourth oil chamber;
fig. 3 is a schematic structural view of a hydraulic machine in embodiment 2 of the present invention;
FIG. 4 is a schematic structural view of a hydraulic machine in embodiment 3 of the present invention;
fig. 5 is a schematic structural view of a hydraulic machine in embodiment 4 of the present invention.
Wherein, the technical characteristics that each reference numeral refers to are as follows:
10. a continuous flow amplifier; 11. a first direction changing valve; 12. a pressure oil connection end; 13. a first pressing element; 14. a second pressing element; 15. an oil return end; 16. a first shuttle valve; 17. an oil outlet end; 21. a flow amplifying cylinder; 22. a housing; 23. a first active lever; 24. a second driving lever; 25. a slave piston; 26. a first oil chamber; 27. a second oil chamber; 28. a third oil chamber; 29. a fourth oil chamber; 31. a first valve; 32. a second valve; 33. a first check valve; 34. a second one-way valve; 35. a first overflow valve; 36. a second overflow valve; 41. an oil supply path; 42. a third check valve; 43. a fourth check valve; 44. an oil tank connecting end; 51. a hydraulic cylinder; 52. a second directional control valve; 53. a second shuttle valve; 54. a third directional control valve; 55. a slider; 56. a fixed block; 57. a hydraulic pump; 58. a safety valve; 59. and a hydraulic oil tank.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is further described in detail with reference to the following embodiments, but the scope of the present invention is not limited to the following embodiments.
Example 1:
referring to fig. 1 and 2, a continuous flow amplifier 10 includes a first direction changing valve 11, a first shuttle valve 16, a flow amplifying cylinder 21, and an oil supply path 41.
The flow rate amplification cylinder 21 includes a housing 22, a first drive lever 23, a second drive lever 24, and a slave piston 25, and a first oil chamber 26, a second oil chamber 27, a third oil chamber 28, and a fourth oil chamber 29 are provided in the housing 22. The driven piston 25 is fixedly connected with the first driving rod 23 and the second driving rod 24 respectively, the first driving rod 23, the second driving rod 24 and the driven piston 25 are slidably mounted in the housing 22, the second oil chamber 27 and the third oil chamber 28 are located on two sides of the driven piston 25 in the sliding direction respectively, and the diameters of the first driving rod 23 and the second driving rod 24 are the same. The first active lever 23 extends into the first oil chamber 26, and the second active lever 24 extends into the fourth oil chamber 29. The first active lever 23 blocks a gap between the first oil chamber 26 and the second oil chamber 27, the second active lever 24 blocks a gap between the third oil chamber 28 and the fourth oil chamber 29, and the slave piston 25 blocks a gap between the second oil chamber 27 and the third oil chamber 28, thereby sealing the first oil chamber 26, the second oil chamber 27, the third oil chamber 28, and the fourth oil chamber 29 from each other. The cross-sectional area of the first driving lever 23 is smaller than the difference between the cross-sectional area of the slave piston 25 and the cross-sectional area of the second driving lever 24, and the cross-sectional area of the second driving lever 24 is smaller than the difference between the cross-sectional area of the slave piston 25 and the cross-sectional area of the first driving lever 23.
The first oil chamber 26 and the fourth oil chamber 29 are respectively communicated with the first direction valve 11, the first direction valve 11 is provided with a pressure oil connecting end 12 and an oil return end 15, the first direction valve 11 can be an electromagnetic direction valve or a hydraulic control direction valve, and the first direction valve 11 is a two-position four-way electromagnetic direction valve in the embodiment. The first reversing valve 11 is provided with 4 ports including a port a, a port b, a port p and a port t, wherein the port a is communicated with the first oil chamber 26, the port b is communicated with the fourth oil chamber 29, the port p is communicated with the pressure oil connecting end 12, and the port t is communicated with the oil return end 15. The housing 22 is fixedly provided with a first pressing element 13 and a second pressing element 14, the first pressing element 13 is located in the first oil chamber 26 and is abutted against the first driving rod 23, the second pressing element 14 is located in the fourth oil chamber 29 and is abutted against the second driving rod 24, and the first pressing element 13 and the second pressing element 14 are respectively connected with the first reversing valve 11. The first pressure element 13 and the second pressure element 14 both adopt travel switches, and the first pressure element 13 and the second pressure element 14 are respectively electrically connected with the first reversing valve 11.
The second oil chamber 27 and the third oil chamber 28 are respectively communicated with 2 oil inlets of the first shuttle valve 16, the oil supply path 41 is provided with a third one-way valve 42 and a fourth one-way valve 43, two ends of the third one-way valve 42 are respectively communicated with the oil supply path 41 and the second oil chamber 27, and two ends of the fourth one-way valve 43 are respectively communicated with the oil supply path 41 and the third oil chamber 28. The first shuttle valve 16 is provided with an oil outlet end 17.
The oil supply passage 41 communicates with the second oil chamber 27 and the third oil chamber 28, respectively. The first oil chamber 26 and the second oil chamber 27 are respectively communicated with the first shuttle valve 16, a first valve 31 is arranged between the first oil chamber 26 and the first shuttle valve 16, a second valve 32 is arranged between the fourth oil chamber 29 and the first shuttle valve 16, a first one-way valve 33 is arranged between the first oil chamber 26 and the first reversing valve 11, and a second one-way valve 34 is arranged between the fourth oil chamber 29 and the first reversing valve 11. The first valve 31 and the second valve 32 are both pilot-operated valves, and a pilot end of the first valve 31 communicates with the fourth oil chamber 29, and a pilot end of the second valve 32 communicates with the first oil chamber 26. The first oil chamber 26 is communicated with a first overflow valve 35, the fourth oil chamber 29 is communicated with a second overflow valve 36, the first overflow valve 35 and the second overflow valve 36 are both communicated with an oil supply oil path 41, the oil supply oil path 41 is provided with an oil tank connecting end 44, and the oil return end 15 is communicated with the oil supply oil path 41.
The specific working process is as follows:
in the initial state, the port p communicates with the port a, the port t communicates with the port b, and the first valve 31 and the second valve 32 are closed. Hydraulic oil having a large pressure flows into the first oil chamber 26 through the pressure oil connection end 12, the port p, the port a, and the first check valve 33, and the first driving rod 23 is pushed by the pressure of the hydraulic oil in the first oil chamber 26 to drive the driven piston 25 and the second driving rod 24 to move in a direction away from the first oil chamber 26. The slave piston 25 and the second driving lever 24 push the hydraulic oil in the third oil chamber 28 and the fourth oil chamber 29, respectively, during the movement, so that the hydraulic oil in the third oil chamber 28 can flow to the first shuttle valve 16. When the hydraulic oil with a larger pressure is introduced into the first oil chamber 26, the hydraulic oil is introduced into the control end of the second valve 32, so that the second valve 32 is opened, and through the arrangement of the second check valve 34, the hydraulic oil in the fourth oil chamber 29 is pushed out by the second active lever 24 and flows into the first shuttle valve 16 through the second valve 32, so that the hydraulic oil is discharged through the first shuttle valve 16 and the oil outlet end 17, and the function of increasing the output flow rate of the hydraulic oil is realized. The slave piston 25 sucks in hydraulic oil through the oil supply passage 41 and the tank connection end 44 while moving.
When the first driving rod 23 drives the second driving rod 24 to move and the second driving rod 24 presses the second pressure element 14, the first direction valve 11 is triggered to switch to the connection between the port p and the port b, the port t is connected to the port b, and the second valve 32 is closed due to the loss of pressure oil at the control end. Hydraulic oil having a relatively large pressure flows into the fourth oil chamber 29 through the pressure oil connection end 12, the port p, the port b and the second check valve 34, and the second driving rod 24 is pushed by the pressure of the hydraulic oil in the fourth oil chamber 29 to drive the driven piston 25 and the first driving rod 23 to move in a direction away from the fourth oil chamber 29. The slave piston 25 and the first driving lever 23 push the hydraulic oil in the second oil chamber 27 and the first oil chamber 26, respectively, during the movement, so that the hydraulic oil in the third oil chamber 28 can flow to the first shuttle valve 16. When hydraulic oil with a relatively high pressure is introduced into the fourth oil chamber 29, the hydraulic oil is introduced into the control end of the first valve 31, so that the first valve 31 is opened, and the hydraulic oil in the fourth oil chamber 29 is pushed out by the first driving rod 23 and flows into the first shuttle valve 16 through the first valve 31 by the arrangement of the first check valve 33, so that the hydraulic oil is discharged through the first shuttle valve 16 and the oil outlet end 17, thereby realizing the function of increasing the output flow of the hydraulic oil, and the driven piston 25 sucks in the hydraulic oil through the oil supply oil path 41 and the oil tank connecting end 44 while moving.
When the second driving rod 24 drives the first driving rod 23 to move and the first driving rod 23 extrudes the first pressure-operated element 13, the first reversing valve 11 is triggered to switch to the p port to be communicated with the a port, and the t port is communicated with the b port, the first valve 31 is closed because the control end loses pressure oil, and when hydraulic oil with larger pressure is introduced into the fourth oil chamber 29, the hydraulic oil is introduced into the control end of the first valve 31, so that the first valve 31 is opened. Thereby realizing continuous circulation work of the flow amplifier.
The flow amplification factor k of the continuous flow amplifier 10 is Q2/Q1＝D2/d2. Wherein Q2Is the flow rate, Q, of the oil outlet end 171D is the diameter of the slave piston 25 and D is the diameter of the first and second driving levers 23 and 24 for the flow rate of the pressure oil connection 12.
The embodiment has the following advantages:
the hydraulic oil flows into the first oil chamber 26 through the pressure oil connecting end 12 and the first reversing valve 11, the hydraulic oil in the first oil chamber 26 pushes the first driving rod 23 to move, the first driving rod 23 drives the driven piston 25 and the second driving rod 24 to move towards the direction far away from the first oil chamber 26, and the driven piston 25 pushes the hydraulic oil in the third oil chamber 28 to be discharged through the first shuttle valve 16 and the oil outlet end 17 in the moving process. Since the cross-sectional area of the first driving lever 23 is smaller than the difference between the cross-sectional area of the slave piston 25 and the cross-sectional area of the second driving lever 24, the flow rate of the hydraulic oil discharged from the third oil chamber 28 is larger than the flow rate of the hydraulic oil entering the first oil chamber 26, and the function of increasing the flow rate is realized.
Then, the communication state of the first reversing valve 11 is switched, so that the hydraulic oil flows into the second oil chamber 27 through the pressure oil connecting end 12 and the first reversing valve 11, the hydraulic oil in the second oil chamber 27 pushes the second driving rod 24 to move, the second driving rod 24 drives the driven piston 25 and the first driving rod 23 to move in the direction away from the second oil chamber 27, and the driven piston 25 pushes the hydraulic oil in the second oil chamber 27 to be discharged through the first shuttle valve 16 and the oil outlet end 17 during the moving process. Since the cross-sectional area of the second driving lever 24 is smaller than the difference between the cross-sectional area of the slave piston 25 and the cross-sectional area of the first driving lever 23, the flow rate of the hydraulic oil discharged from the second oil chamber 27 is made larger than the flow rate of the hydraulic oil entering the second oil chamber 27, and the flow rate increasing function is realized.
In the process that the driven piston 25 pushes the hydraulic oil in the third oil chamber 28 to flow to the first shuttle valve 16, the volume of the second oil chamber 27 is increased and the hydraulic oil is sucked through the oil supply oil path 41, and then the communication state of the first direction changing valve 11 is switched to make the driven piston 25 move reversely and push the hydraulic oil in the second oil chamber 27 to flow to the first shuttle valve 16, while the volume of the third oil chamber 28 is increased and the hydraulic oil is sucked through the oil supply oil path 41. Therefore, by repeatedly switching the communication state of the first reversing valve 11, pressure oil can be respectively injected into the first oil chamber 26 and the fourth oil chamber 29, the first driving rod 23, the second driving rod 24 and the driven piston 25 are pushed to move in a reciprocating manner, the function of continuously discharging hydraulic oil is further realized, and the effect of continuous flow amplification is achieved.
The continuous flow amplifier 10 has no throttling loss and overflow loss when in normal operation, and the one-way valve and the first shuttle valve 16 can adopt conical valve cores, so that the continuous flow amplifier has the advantage of good sealing property, reduces the leakage of hydraulic oil, has small overall energy loss, achieves the advantage of high energy efficiency, and can effectively reduce energy consumption.
The flow is automatically and continuously amplified, so that the hydraulic system does not need to be provided with an extra energy accumulator, a pump, a motor and a differential connection flow increasing device, the arrangement structure of the hydraulic system is simpler, the use requirement is met, the manufacturing cost is effectively reduced, the leakage probability of hydraulic oil is reduced, and the effect of improving the sealing property is achieved.
Because the hydraulic system does not need to be provided with additional equipment such as an energy accumulator, a pump, a motor and the like, the hydraulic system is favorable for controlling the pressure of hydraulic oil, and the internal pressure of the hydraulic system is smaller, so that the hydraulic system does not need to be designed with an overhigh sealing grade in the design and manufacture process, the hydraulic system is convenient to design and manufacture, and meanwhile, hydraulic system elements with lower sealing grade and cheaper price can be selected, so that the manufacturing cost can be further reduced.
The continuous flow amplifier 10 is very reliable during operation due to the low pressure inside the hydraulic system. The first pressure element 13 and the second pressure element 14 directly control the switching of the communication state of the first reversing valve 11, thereby effectively reducing the complexity of the system, further reducing the probability of failure and further improving the reliability. The advantages of high efficiency, good sealing performance, stability, reliability and lower cost are achieved.
By switching the opening and closing of the first valve 31 and the second valve 32, the hydraulic oil in the first oil chamber 26 and the fourth oil chamber 29 can flow to the first shuttle valve 16, and the flow rate of the oil outlet port 17 is increased, thereby achieving the effect of amplifying the flow rate of the hydraulic oil. And the hydraulic oil of the first and fourth oil chambers 26 and 29 is prevented from flowing to the first direction switching valve 11 by the provision of the first and second check valves 33 and 34.
When pressurized oil is introduced into the first chamber 26, the pressurized oil enters the control end of the second valve 32, causing the second valve 32 to open. The pressure oil in the first oil chamber 26 pushes the first active lever 23 to drive the second active lever 24 to push out the hydraulic oil in the fourth oil chamber 29, so that the hydraulic oil in the fourth oil chamber 29 enters the first shuttle valve 16 through the second valve 32. When the pressurized oil is introduced into the second oil chamber 27, the pressurized oil enters the control end of the first valve 31, so that the first valve 31 is opened. The pressure oil in the second oil chamber 27 pushes the second active lever 24 to drive the first active lever 23 to push out the hydraulic oil in the first oil chamber 26, so that the hydraulic oil in the first oil chamber 26 enters the first shuttle valve 16 through the first valve 31. The function of automatically controlling the opening and closing of the first valve 31 and the second valve 32 according to the pressure oil in the first oil chamber 26 and the second oil chamber 27 is realized.
When the first driving rod 23 and the second driving rod 24 respectively extrude the first pressing element 13 and the second pressing element 14, the first pressing element 13 and the second pressing element 14 can respectively trigger the first reversing valve 11 to switch the communication state, so that the communication state of the first reversing valve 11 can be automatically switched according to the movement of the first driving rod 23 and the second driving rod 24, the continuous flow amplifier 10 can automatically and continuously amplify the flow, and the effects of convenience in use and efficiency improvement are achieved.
By the provision of the third check valve 42 and the fourth check valve 43, the slave piston 25 can be prevented from flowing into the oil supply passage 41 in the process of pushing the hydraulic oil out of the second oil chamber 27 and the third oil chamber 28, respectively, and the flow rate of the hydraulic oil at the oil outlet port 17 can be ensured to be stable.
Through the arrangement of the first relief valve 35 and the second relief valve 36, when the hydraulic oil pressure in the first oil chamber 26 and the second oil chamber 27 is too high, the hydraulic oil pressure in the first oil chamber 26 and the second oil chamber 27 is prevented from being too high, and the effects of improving safety and reliability of a hydraulic system are achieved.
When the first reversing valve 11 is switched to the communicated state, the pipeline communicated with the pressure oil connecting end 12 is disconnected to discharge pressure oil into the oil return pipeline, so that the situation that the hydraulic oil in the first oil cavity 26 and the fourth oil cavity 29 is equal to cause that the hydraulic oil cannot push the first driving rod 23, the second driving rod 24 and the driven piston 25 to move is prevented, the oil pressure in the two oil inlets of the first shuttle valve 16 is prevented from being equal, and the function of improving the running reliability of equipment is achieved.
The tank connection end 44 communicates with the hydraulic tank 59 so that the oil supply path 41 can be supplied with oil via the hydraulic tank 59, ensuring that sufficient hydraulic oil is drawn into the second and third oil chambers 27 and 28 in the oil supply path 41. When the relief valves of the first relief valve 35 and the second relief valve 36 flow into the oil supply passage 41, the excess hydraulic oil can flow back into the hydraulic oil tank 59 through the tank connection end 44, thereby preventing the hydraulic oil in the oil supply passage 41 from being excessively high in pressure, and improving safety and reliability.
Example 2:
referring to fig. 3, a hydraulic press includes a hydraulic cylinder 51, a slider 55, a fixed block 56, a pressure oil supply device, and the continuous flow amplifier 10 in embodiment 1, wherein the slider 55 is fixedly mounted on the hydraulic cylinder 51, a pressure oil connection end 12 of the continuous flow amplifier 10 is communicated with the pressure oil supply device, and an oil outlet end 17 of the continuous flow amplifier 10 is communicated with the hydraulic cylinder 51. The pressure oil supply device is communicated with a hydraulic oil tank 59, the pressure oil supply device comprises a hydraulic pump 57 and a safety valve 58, the hydraulic pump 57 is respectively communicated with the continuous flow amplifier 10, the second shuttle valve 53 and the hydraulic oil tank 59, and the safety valve 58 is communicated with the hydraulic pump 57. A workpiece is placed between the sliding block 55 and the fixed block 56, and the hydraulic cylinder 51 drives the sliding block 55 to move towards the fixed block 56 and extrude the workpiece, so that the function of processing the workpiece is realized.
The embodiment has the following advantages:
the hydraulic pump 57 inputs the hydraulic oil in the hydraulic oil tank 59 into the continuous flow amplifier 10, amplifies the output flow of the hydraulic oil through the continuous flow amplifier 10, inputs the hydraulic oil with a larger flow into the hydraulic cylinder 51, drives the hydraulic cylinder 51 to move rapidly, and achieves the effect of improving the working efficiency of the hydraulic machine.
Example 3:
referring to fig. 4, a hydraulic machine includes a hydraulic cylinder 51, a slide block 55, a fixed block 56, a pressure oil supply device, a second directional valve 52, a second shuttle valve 53, and the continuous flow amplifier 10 in embodiment 1, the slide block 55 is fixedly installed on the hydraulic cylinder 51, the second directional valve 52 is a three-position four-way electromagnetic directional valve, and the second directional valve 52 includes a left position, a middle position, and a right position. The second direction valve 52 is provided on a pipe between the continuous flow rate amplifier 10 and the pressure oil supply device, and the second shuttle valve 53 is provided on a pipe between the continuous flow rate amplifier 10 and the hydraulic cylinder 51. The pressure oil supply device is communicated with the second reversing valve 52, the pressure oil connecting end 12 of the continuous flow amplifier 10 is communicated with the second reversing valve 52, and 2 oil inlets of the second shuttle valve 53 are respectively communicated with the oil outlet end 17 of the continuous flow amplifier 10 and the second reversing valve 52. The pressure oil supply device is communicated with a hydraulic oil tank 59, the pressure oil supply device comprises a hydraulic pump 57 and a safety valve 58, the hydraulic pump 57 is respectively communicated with the continuous flow amplifier 10, the second shuttle valve 53 and the hydraulic oil tank 59, and the safety valve 58 is communicated with the hydraulic pump 57. The second direction valve 52 communicates with a hydraulic oil tank 59. A workpiece is placed between the sliding block 55 and the fixed block 56, and the hydraulic cylinder 51 drives the sliding block 55 to move towards the fixed block 56 and extrude the workpiece, so that the function of processing the workpiece is realized.
The embodiment has the following advantages:
when the second direction valve 52 is switched to the neutral position, the hydraulic pump 57 is not communicated with the second shuttle valve 53 and the continuous flow rate amplifier 10, thereby stopping the movement of the hydraulic cylinder 51. When the second direction changing valve 52 is switched to the left position, the pressure oil supply device supplies hydraulic oil to the second shuttle valve 53 through the second direction changing valve 52, so that the hydraulic cylinder 51 is operated at a slower speed. When the second directional valve 52 is switched to the right position, the output flow rate of the hydraulic oil is amplified by the continuous flow amplifier 10, so that the hydraulic cylinder 51 is accelerated at a faster speed. When the work is stopped, the second reversing valve 52 is switched to the middle position, so that the hydraulic cylinder 51 stops moving; when the hydraulic cylinder 51 works, the pressure of hydraulic oil is higher, so that the thrust of the hydraulic cylinder 51 is also higher, and the hydraulic cylinder is suitable for providing a working condition that the thrust compresses a workpiece; when the hydraulic cylinder 51 needs to be driven to move rapidly, the state can be switched to a fast forward state, the working efficiency is improved, and the method has the advantage of high applicability.
Example 4:
referring to fig. 5, a hydraulic press includes a hydraulic cylinder 51, a slide block 55, a fixed block 56, a pressure oil supply device, a second directional valve 52, a third directional valve 54, a second shuttle valve 53 and the continuous flow amplifier 10 of embodiment 1, the slide block 55 is fixedly mounted on the hydraulic cylinder 51, the pressure oil supply device is communicated with the second directional valve 52, the pressure oil connection end 12 of the continuous flow amplifier 10 is communicated with the second directional valve 52, 2 oil inlets of the second shuttle valve 53 are respectively communicated with the oil outlet end 17 of the continuous flow amplifier 10 and the second directional valve 52, the pressure oil supply device is communicated with a hydraulic oil tank 59, the pressure oil supply device includes a hydraulic pump 57 and a safety valve 58, the hydraulic pump 57 is respectively communicated with the continuous flow amplifier 10, the second shuttle valve 53 and the hydraulic oil tank 59, and the safety valve 58 is communicated with the hydraulic pump 57. The third direction changing valve 54 is provided on a line between the second shuttle valve 53 and the hydraulic cylinder 51, an output end of the second shuttle valve 53 communicates with the third direction changing valve 54, and both the second direction changing valve 52 and the third direction changing valve 54 communicate with the hydraulic oil tank 59. A workpiece is placed between the sliding block 55 and the fixed block 56, and the hydraulic cylinder 51 drives the sliding block 55 to move towards the fixed block 56 and extrude the workpiece, so that the function of processing the workpiece is realized.
The third directional valve 54 is a two-position, four-way electromagnetic directional valve, and the third directional valve 54 includes an upper position and a lower position.
When the third directional control valve 54 is shifted to the upper position, the hydraulic pump 57 can supply hydraulic oil to the rodless chamber of the hydraulic cylinder 51, causing the hydraulic cylinder 51 to move in the forward direction. When the second directional control valve 52 is shifted to the lower position, the hydraulic pump 57 can supply hydraulic oil to the rod chambers of the hydraulic cylinders 51, and the hydraulic cylinders 51 are moved in the opposite direction.
In combination with the continuous flow amplifier 10, the second reversing valve 52 and the third reversing valve 54, the hydraulic machine is capable of switching 5 different operating states:
1. when the hydraulic cylinder 51 is required to stop moving, the second reversing valve 52 is switched to a middle position, and the hydraulic pump 57 is unloaded;
2. when the hydraulic cylinder 51 needs to move in the fast forward direction (fast forward state), the second reversing valve 52 is switched to the right position, the third reversing valve 54 is switched to the upper position, the hydraulic pump 57 amplifies the flow through the continuous flow amplifier 10 and supplies oil to the hydraulic cylinder 51, and the hydraulic cylinder 51 drives the slide block 55 to move in the fast forward direction;
3. when the hydraulic cylinder 51 needs to move forward at a low speed (in a working state), the second reversing valve 52 is switched to the left position, the third reversing valve 54 is switched to the upper position, the hydraulic pump 57 directly supplies oil to the hydraulic cylinder 51, and the hydraulic cylinder 51 drives the sliding block 55 to move forward at a low speed;
4. when the hydraulic cylinder 51 needs to move reversely at a low speed (in a slow return state), the second reversing valve 52 is switched to the left position, the third reversing valve 54 is switched to the lower position, the hydraulic pump 57 directly supplies oil to the hydraulic cylinder 51, and the hydraulic cylinder 51 drives the slide block 55 to move reversely at a low speed;
5. when the hydraulic cylinder 51 needs to move reversely (fast return state), the second directional valve 52 is switched to the right position, the third directional valve 54 is switched to the lower position, the hydraulic pump 57 amplifies the flow through the continuous flow amplifier 10 and supplies oil to the hydraulic cylinder 51, and the hydraulic cylinder 51 drives the slide block 55 to move reversely.
The embodiment has the following advantages:
therefore, various different working states are realized, different working states can be adapted, different use requirements are met, and the effects of improving the applicability and the production efficiency are achieved.
Variations and modifications to the above-described embodiments may occur to those skilled in the art, which fall within the scope and spirit of the above description. Therefore, the present invention is not limited to the specific embodiments disclosed and described above, and some modifications and variations of the present invention should fall within the scope of the claims of the present invention. Furthermore, although specific terms are employed herein, they are used in a generic and descriptive sense only and not for purposes of limitation.
Claims (10)
1. A continuous flow amplifier (10) comprising a first directional valve (11) and a first shuttle valve (16), characterized by: the oil pump further comprises a flow amplification cylinder (21) and an oil supply way (41), wherein the flow amplification cylinder (21) comprises a shell (22), a first driving rod (23), a second driving rod (24) and a driven piston (25), a first oil cavity (26), a second oil cavity (27), a third oil cavity (28) and a fourth oil cavity (29) are arranged in the shell (22), the driven piston (25) is fixedly connected with the first driving rod (23) and the second driving rod (24) respectively, the first driving rod (23), the second driving rod (24) and the driven piston (25) are installed in the shell (22) in a sliding mode, the second oil cavity (27) and the third oil cavity (28) are located on two sides of the driven piston (25) in the sliding direction respectively, the first driving rod (23) extends into the first oil cavity (26), and the second driving rod (24) extends into the fourth oil cavity (29), the first oil chamber (26) and the fourth oil chamber (29) are communicated with a first reversing valve (11) respectively, the oil supply oil path (41) is communicated with a second oil chamber (27) and a third oil chamber (28) respectively, the second oil chamber (27) and the third oil chamber (28) are communicated with 2 oil inlets of a first shuttle valve (16) respectively, the first reversing valve (11) is provided with a pressure oil connecting end (12), and the first shuttle valve (16) is provided with an oil outlet end (17).
2. The continuous flow amplifier (10) of claim 1, wherein: the first oil chamber (26) and the second oil chamber (27) are respectively communicated with the first shuttle valve (16), a first valve (31) is arranged between the first oil chamber (26) and the first shuttle valve (16), a second valve (32) is arranged between the fourth oil chamber (29) and the first shuttle valve (16), a first one-way valve (33) is arranged between the first oil chamber (26) and the first reversing valve (11), and a second one-way valve (34) is arranged between the fourth oil chamber (29) and the first reversing valve (11).
3. The continuous flow amplifier (10) of claim 2, wherein: the first valve (31) and the second valve (32) are both hydraulic control valves, the control end of the first valve (31) is communicated with the fourth oil chamber (29), and the control end of the second valve (32) is communicated with the first oil chamber (26).
4. The continuous flow amplifier (10) of claim 1, wherein: casing (22) fixed mounting has first pressure to move component (13) and second pressure to move component (14), first pressure move component (13) be located first oil pocket (26) and with first active lever (23) butt, second pressure move component (14) be located fourth oil pocket (29) and with second active lever (24) butt, first pressure move component (13) and second pressure move component (14) and be connected with first switching-over valve (11) respectively.
5. The continuous flow amplifier (10) of claim 1, wherein: the oil supply oil way (41) is provided with a third one-way valve (42) and a fourth one-way valve (43), two ends of the third one-way valve (42) are respectively communicated with the oil supply oil way (41) and the second oil cavity (27), and two ends of the fourth one-way valve (43) are respectively communicated with the oil supply oil way (41) and the third oil cavity (28).
6. The continuous flow amplifier (10) of claim 1, wherein: the first oil cavity (26) is communicated with a first overflow valve (35), the fourth oil cavity (29) is communicated with a second overflow valve (36), and the first overflow valve (35) and the second overflow valve (36) are both communicated with an oil supply oil way (41).
7. The continuous flow amplifier (10) of claim 6, wherein: the first reversing valve (11) is provided with an oil return end (15), and the oil return end (15) is communicated with an oil supply oil way (41).
8. A hydraulic machine comprising a hydraulic cylinder (51) and a pressure oil supply device, characterized in that: the continuous flow amplifier (10) as claimed in any one of claims 1 to 7, wherein the pressure oil connection end (12) of the continuous flow amplifier (10) is in communication with a pressure oil supply, and the oil outlet end (17) of the continuous flow amplifier (10) is in communication with a hydraulic cylinder (51).
9. The hydraulic machine as recited in claim 8 wherein: the hydraulic control system is characterized by further comprising a second reversing valve (52) and a second shuttle valve (53), wherein the second reversing valve (52) is arranged on a pipeline between the continuous flow amplifier (10) and the pressure oil supply device, the second shuttle valve (53) is arranged on a pipeline between the continuous flow amplifier (10) and the hydraulic cylinder (51), 2 oil inlets of the second shuttle valve (53) are respectively communicated with the oil outlet end (17) of the continuous flow amplifier (10) and the second reversing valve (52), the pressure oil supply device is communicated with a hydraulic oil tank (59), and the second reversing valve (52) is communicated with the hydraulic oil tank (59).
10. The hydraulic machine as recited in claim 8 wherein: the hydraulic control system further comprises a third reversing valve (54), wherein the third reversing valve (54) is arranged on a pipeline between the continuous flow amplifier (10) and the hydraulic cylinder (51).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111332922.9A CN113883108A (en) | 2021-11-11 | 2021-11-11 | Continuous flow amplifier and hydraulic press |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111332922.9A CN113883108A (en) | 2021-11-11 | 2021-11-11 | Continuous flow amplifier and hydraulic press |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113883108A true CN113883108A (en) | 2022-01-04 |
Family
ID=79017238
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111332922.9A Pending CN113883108A (en) | 2021-11-11 | 2021-11-11 | Continuous flow amplifier and hydraulic press |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113883108A (en) |
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2021
- 2021-11-11 CN CN202111332922.9A patent/CN113883108A/en active Pending
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