Pressurizing and accelerating hydraulic system

Abstract

The utility model belongs to the technical field of hydraulic pressure, and discloses a pressurizing and accelerating hydraulic system. Aiming at the problems that a traditional hydraulic system is insufficient in pressure, low in efficiency and large in energy consumption, the pressurizing module and the automatic reciprocating pressurizer are additionally arranged, and the pressure and flow of the system are remarkably improved. The system comprises a low-pressure system, a supercharging module and an automatic reciprocating supercharger, the low-pressure system stores and pumps hydraulic oil, the supercharging module accurately controls oil pressure and flow, and the automatic reciprocating supercharger supercharges low-pressure oil and then outputs the supercharged low-pressure oil. The system is high in output pressure and large in flow, meets the requirements of high-pressure and large-flow working conditions, and improves the working efficiency; the balance valve and the hydraulic lock achieve pressure maintaining and speed increasing, energy consumption is reduced through the design of the variable pump and the supercharger, the structure is compact, maintenance is convenient, application is wide, and the performance of hydraulic equipment is remarkably improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to the technical field of hydraulic pressure, especially to a pressure increasing and speed increasing hydraulic system. BACKGROUND

[0002] In the technical field of hydraulic pressure, the traditional hydraulic system often has problems such as insufficient pressure, low efficiency, and large energy consumption. For example, in some application scenarios that require high pressure and large flow rate, such as hydraulic machines, hydraulic lifting platforms, hydraulic excavators, and other equipment, the traditional hydraulic system is difficult to meet the demand for high pressure and high flow rate, resulting in low equipment working efficiency and increased energy consumption. In addition, the traditional hydraulic system also has deficiencies in pressure maintenance and speed increase, making it difficult to meet the requirements of some special working conditions. SUMMARY

[0003] The utility model aims at providing a pressure increasing and speed increasing hydraulic system to solve the technical problem that the traditional hydraulic system cannot simultaneously meet the demand for high pressure and high flow rate, and has poor pressure maintenance and speed increase performance.

[0004] To achieve the above-mentioned purpose, the utility model adopts the technical scheme of providing a pressure increasing and speed increasing hydraulic system, which comprises:

[0005] A low-pressure system is provided with a reversing valve, the oil outlet of the low-pressure system is connected to the P0 port of the reversing valve, and the oil return port of the low-pressure system is connected to the T0 port of the reversing valve.

[0006] A pressure increasing module is provided, which comprises a balance valve, a reverse hydraulic lock, a forward hydraulic lock, and an automatic reciprocating pressure increaser. The balance valve is arranged on the pipeline connecting the AO port of the reversing valve and the rod cavity of the oil cylinder. The K port of the balance valve is in communication with the B0 port of the reversing valve. The forward hydraulic lock is arranged on the pipeline connecting the B0 port of the reversing valve and the rodless cavity of the oil cylinder. The oil inlet of the reverse hydraulic lock is connected to the rod cavity of the oil cylinder, the oil outlet of the reverse hydraulic lock is connected to the oil inlet of the forward hydraulic lock, the AO port of the reversing valve is connected to the feedback port of the reverse hydraulic lock and the feedback port of the forward hydraulic lock through a pipeline. The low-pressure cavity of the automatic reciprocating pressure increaser is connected to the rod cavity of the oil cylinder through a pipeline, the high-pressure cavity of the automatic reciprocating pressure increaser is connected to the oil outlet of the reverse hydraulic lock through a pipeline, and the high-pressure oil outlet of the automatic reciprocating pressure increaser is connected to the rodless cavity of the oil cylinder.

[0007] In one embodiment, the low-pressure system comprises an oil tank for storing hydraulic oil and an oil pump. The input end of the oil pump is connected to the oil tank, the output end of the oil pump is connected to the P0 port of the reversing valve, and the T0 port of the reversing valve is connected to the oil tank through a pipeline.

[0008] In one embodiment, the forward hydraulic lock and the reverse hydraulic lock are both hydraulic control check valves.

[0009] In one embodiment, the high-pressure oil outlet of the automatic reciprocating supercharger is provided with a check valve, which allows high-pressure oil to flow from the high-pressure cavity of the automatic reciprocating supercharger to the rodless cavity of the oil cylinder, while preventing high-pressure oil in the rodless cavity of the oil cylinder from flowing reversely into the high-pressure cavity of the automatic reciprocating supercharger.

[0010] In one embodiment, the balance valve, the reverse hydraulic lock, the forward hydraulic lock and the automatic reciprocating supercharger in the supercharging module are all modularly designed, and are connected through a jack or a flange or a pipeline.

[0011] The one or more technical solutions in the above embodiments of the utility model have at least the following technical effects or advantages:

[0012] The supercharging and speed-increasing hydraulic system provided in the embodiments of the utility model adopts automatic reciprocating supercharging, has strong versatility, and can meet the high-pressure flow requirements of different hydraulic systems by only changing the low-pressure oil inlet flow. BRIEF DESCRIPTION OF DRAWINGS

[0013] In order to more clearly illustrate the technical solutions in the embodiments of the utility model, the following will briefly introduce the drawings needed to be used in the embodiments or the prior art description. Obviously, the drawings in the following description are only some embodiments of the utility model, and those skilled in the art can also obtain other drawings according to these drawings without creative labor.

[0014] Figure 1 The structure schematic diagram of the supercharging and speed-increasing hydraulic system provided in the embodiments of the utility model.

[0015] Among them, various signs are as follows:

[0016] 1, low pressure system;2, supercharging module;3, oil cylinder;11, reversing valve;21, balance valve;22, reverse hydraulic lock;23, forward hydraulic lock;24, automatic reciprocating supercharger. DETAILED DESCRIPTION

[0017] The embodiments of the utility model will be described in detail below, and the examples of the embodiments are shown in the drawings, wherein the same or similar signs represent the same or similar elements or elements with the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and are intended to explain the utility model, and cannot be understood as a limitation of the utility model.

[0018] In the description of the utility model, it is necessary to understand that the orientation or positional relationship indicated by the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like is the orientation or positional relationship shown based on the drawings, and is only for the convenience of describing the utility model and simplifying the description, and therefore cannot be understood as indicating or implying that the devices or elements indicated must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the utility model.

[0019] In addition, the terms "first", "second" are only for the purpose of description, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features.

[0020] In the utility model, unless otherwise explicitly specified and limited, the terms "mounting", "connection", "connection", "fixing" and the like should be understood in a broad sense, for example, it can be fixed connection, or detachable connection, or integrated; it can be mechanical connection, or electrical connection; it can be directly connected, or indirectly connected through intermediate medium, or the communication or interaction relationship between two elements. For ordinary skilled persons in the art, the specific meaning of the above terms in the utility model can be understood according to the specific circumstances.

[0021] Please refer to Figure 1 The embodiment of the application provides a kind of pressure increasing speed increasing hydraulic system, including low pressure system 1, pressure increasing module 2.Wherein, reversing valve 11 is provided in low pressure system 1, the oil outlet of low pressure system 1 is connected with the P0 port of reversing valve 11, and the oil return port of low pressure system 1 is connected with the T0 port of reversing valve 11.Pressure increasing module 2 includes balance valve 21, reverse hydraulic lock 22, positive hydraulic lock 23, automatic reciprocating pressure booster 24;Balance valve 21 is arranged on the pipeline that AO port of reversing valve 11 and the rod cavity of oil cylinder 3 are connected, and the K port of balance valve 21 is connected with the B0 port of reversing valve 11;Positive hydraulic lock 23 is arranged on the pipeline that B0 port of reversing valve 11 and the rodless cavity of oil cylinder 3 are connected;The oil inlet of reverse hydraulic lock 22 is communicated with the rod cavity of oil cylinder 3, the oil outlet of reverse hydraulic lock 22 is communicated with the oil inlet of positive hydraulic lock 23, and the AO port of reversing valve 11 is communicated with the control port of reverse hydraulic lock 22 and the control port of positive hydraulic lock 23 by pipeline;The low pressure cavity of automatic reciprocating pressure booster 24 is communicated with the rod cavity of oil cylinder 3 by pipeline, the high pressure cavity of automatic reciprocating pressure booster 24 is communicated with the oil outlet of reverse hydraulic lock 22 by pipeline, and the high pressure oil outlet of automatic reciprocating pressure booster 24 is communicated with the rodless cavity of oil cylinder 3.

[0022] The working principle is as follows:

[0023] When the low-pressure system 1 reversing valve 11 is reversed to the left position (P0 port is connected to B0 port, and A0 port is connected to T0 port) Figure 1 When the low-pressure system 1 reversing valve 11 is reversed to the left position (P0 port is connected to B0 port, and A0 port is connected to T0 port)

[0024] When the cylinder 3 advances, the oil in the rod cavity of the cylinder 3 needs to pass through the balance valve 21 to the A0 port of the reversing valve 11, and then to the T0 port. When the idle stroke pressure is low, the balance valve 21 is not opened, and the oil in the rod cavity of the cylinder 3 passes through the reverse hydraulic lock 22 to the right, and then passes through the forward hydraulic lock 23 to the rodless cavity of the cylinder 3, realizing speed-up advance. At this time, since the pressure in the rod cavity of the cylinder 3 is greater than the pressure in the rodless cavity, the pressure in the T port (connecting the low-pressure cavity of the automatic reciprocating intensifier 24) of the automatic reciprocating intensifier 24 is greater than the pressure in the P port (connecting the high-pressure cavity of the automatic reciprocating intensifier 24), so the intensifier cannot reciprocate, and no pressure is increased, and no hydraulic oil is consumed.

[0025] When the cylinder 3 advances, the oil in the rod cavity of the cylinder 3 needs to pass through the balance valve 21 to the A0 port of the reversing valve 11, and then to the T0 port. When the idle stroke pressure is low, the balance valve 21 is not opened, and the oil in the rod cavity of the cylinder 3 passes through the reverse hydraulic lock 22 to the right, and then passes through the forward hydraulic lock 23 to the rodless cavity of the cylinder 3, realizing speed-up advance. At this time, since the pressure in the rod cavity of the cylinder 3 is greater than the pressure in the rodless cavity, the pressure in the T port (connecting the low-pressure cavity of the automatic reciprocating intensifier 24) of the automatic reciprocating intensifier 24 is greater than the pressure in the P port (connecting the high-pressure cavity of the automatic reciprocating intensifier 24), so the intensifier cannot reciprocate, and no pressure is increased, and no hydraulic oil is consumed.

[0026] Since the automatic reciprocating intensifier 24 is a continuous reciprocating output of high-pressure oil, the high-pressure output oil quantity is proportional to the low-pressure input flow, and also proportional to the length of the pressure increasing time, so the same automatic reciprocating intensifier 24 can meet the pressure casting machine system with different flow requirements.

[0027] At the same time, when the high-pressure oil outlet (HP) of the automatic reciprocating intensifier 24 has a slight leakage, the leakage of the high-pressure oil can be continuously supplemented by low-pressure oil, so that the automatic reciprocating pressure of the intensifier is realized, and the high-pressure pressure maintaining is continued. However, after the stroke of the traditional pressure cylinder reaches the bottom, the hydraulic oil leaked from the high-pressure cannot be continuously supplemented, and the long-time pressure maintaining cannot be realized.

[0028] When the pressure increases to the appropriate pressure, the reversing valve 11 is reversed to the middle position (as shown in the state of Figure 1 The forward hydraulic lock 23 realizes pressure maintaining.

[0029] When the reversing valve 11 is reversed to the right position, the low-pressure hydraulic oil passes through the internal one-way valve of the balance valve 21 to the rod cavity of the cylinder 3, and at the same time, the A0 port pressure reaches the reverse hydraulic lock 22, so that the reverse hydraulic lock 22 is closed. At the same time, the A0 port pressure is fed back to the forward hydraulic lock 23, so that the forward hydraulic lock 23 is opened.

[0030] The rodless cavity of the oil cylinder 3 returns oil through the opened positive hydraulic lock 23 to the B0 port, and then to the T0 port to return to the oil tank, thereby realizing the retreat of the oil cylinder 3.

[0031] In one embodiment, the low-pressure system 1 comprises an oil tank for storing hydraulic oil and an oil pump, the input end of the oil pump being communicated with the oil tank, and the output end of the oil pump being connected to the P0 port of the reversing valve 11, and the T0 port of the reversing valve 11 being connected to the oil tank through a pipeline. The low-pressure system 1 comprises an oil tank and an oil pump, the input end of the oil pump being communicated with the oil tank, and the output end of the oil pump being connected to the P0 port of the reversing valve 11, and the T0 port of the reversing valve 11 being connected to the oil tank through a pipeline. The oil pump pumps the hydraulic oil in the oil tank into the reversing valve 11 to provide a power source for the hydraulic system. The oil returned after the operation of the reversing valve 11 returns to the oil tank through the T0 port, forming a closed loop to realize the recycling of the hydraulic oil. This design ensures that the low-pressure system 1 can continuously and stably supply oil to the hydraulic system, improving the stability and efficiency of the system.

[0032] In one embodiment, the positive hydraulic lock 23 and the reverse hydraulic lock 22 are both hydraulic control check valves. Specifically, the flow direction of the positive hydraulic lock 23 is towards the rodless cavity of the oil cylinder 3, and the flow direction of the reverse hydraulic lock 22 is from left to right. The positive hydraulic lock 23 and the reverse hydraulic lock 22 can control the flow direction of the hydraulic oil, prevent backflow, and improve the stability and efficiency of the system.

[0033] In one embodiment, the high-pressure oil outlet of the automatic reciprocating supercharger 24 is provided with a check valve, which allows high-pressure oil to flow from the high-pressure cavity of the automatic reciprocating supercharger 24 to the rodless cavity of the oil cylinder 3, while preventing high-pressure oil from the rodless cavity of the oil cylinder 3 from flowing back into the high-pressure cavity of the automatic reciprocating supercharger 24, thereby protecting the supercharger and maintaining the system pressure.

[0034] In one embodiment, the balance valve 21, the reverse hydraulic lock 22, the positive hydraulic lock 23, and the automatic reciprocating supercharger 24 in the supercharging module 2 are all designed in a modular manner, and are connected through jacks or flanges or pipelines. The modular design makes the interfaces and sizes between the components standardized, facilitating quick replacement and upgrading. At the same time, the connection between the components through jacks or flanges makes the connection more firm and reliable, improving the stability and life of the system. This design makes the installation, disassembly, and maintenance of the system more convenient and efficient, improving the maintainability and expandability of the system.

[0035] The above is only a preferred embodiment of the present application, and is not intended to limit the present application. Any modification, equivalent replacement, and improvement made within the spirit and principles of the present application shall be included in the protection scope of the present application.

Claims

1. A supercharged super-sped hydraulic system characterized by, The supercharged and speed-increased hydraulic system comprises: a low-pressure system, a reversing valve is arranged in the low-pressure system, an oil outlet of the low-pressure system is connected to a P0 port of the reversing valve, and a return oil port of the low-pressure system is connected to a T0 port of the reversing valve; a supercharging module, the supercharging module comprises a balance valve, a reverse hydraulic lock, a forward hydraulic lock and an automatic reciprocating supercharger, the balance valve is arranged on a pipeline connected between an AO port of the reversing valve and a rod cavity of a cylinder, a K port of the balance valve is connected to a B0 port of the reversing valve, the forward hydraulic lock is arranged on a pipeline connected between the B0 port of the reversing valve and a rodless cavity of the cylinder, an oil inlet of the reverse hydraulic lock is connected to the rod cavity of the cylinder, an oil outlet of the reverse hydraulic lock is connected to an oil inlet of the forward hydraulic lock, the AO port of the reversing valve is connected to a control port of the reverse hydraulic lock and a control port of the forward hydraulic lock, a low-pressure cavity of the automatic reciprocating supercharger is connected to the rod cavity of the cylinder through a pipeline, a high-pressure cavity of the automatic reciprocating supercharger is connected to the oil outlet of the reverse hydraulic lock through a pipeline, and a high-pressure oil outlet of the automatic reciprocating supercharger is connected to the rodless cavity of the cylinder.

2. The supercharged and speed-increased hydraulic system according to claim 1, wherein: the low-pressure system comprises an oil tank for storing hydraulic oil and an oil pump, an input end of the oil pump is connected to the oil tank, an output end of the oil pump is connected to the P0 port of the reversing valve, and the T0 port of the reversing valve is connected to the oil tank through a pipeline.

3. The supercharged and speed-increased hydraulic system according to claim 1, wherein: the forward hydraulic lock and the reverse hydraulic lock are both hydraulic control check valves.

4. The supercharged and speed-increased hydraulic system according to claim 1, wherein: the high-pressure oil outlet of the automatic reciprocating supercharger is provided with a check valve, the check valve allows high-pressure oil to flow from the high-pressure cavity of the automatic reciprocating supercharger to the rodless cavity of the cylinder, and prevents high-pressure oil in the rodless cavity of the cylinder from flowing reversely into the high-pressure cavity of the automatic reciprocating supercharger.

5. The supercharged and speed-increased hydraulic system according to claim 1, wherein: the balance valve, the reverse hydraulic lock, the forward hydraulic lock and the automatic reciprocating supercharger in the supercharging module are all modularized, and the modules are connected through jacks or flanges or pipelines.

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