Modularized hydraulic energy-saving composite adjusting system

Abstract

The invention discloses a modularized hydraulic energy-saving composite regulating system, which relates to the technical field of hydraulic systems and comprises a hydraulic pump source, a flow control valve, a pressure control valve, an electromagnetic directional valve and a differential pressure regulating valve. The oil inlet main pipeline is communicated with the pressure control valve through the pressure overflow pipeline, a control port of the pressure control valve is communicated with the differential pressure regulating valve, and an oil outlet of the differential pressure regulating valve and an oil outlet of the pressure control valve are both communicated with the overflow oil tank. A control port of the differential pressure adjusting valve and a hydraulic system pipeline are connected to two oil outlets of the flow control valve respectively, the pressure overflow pipeline is communicated with the electromagnetic reversing valve through an electromagnetic valve oil inlet pipeline, and the electromagnetic reversing valve is communicated with the flow control valve through a pipeline. By arranging the pressure difference regulating valve, constant pressure difference control over flow can be achieved, and the constant pressure difference control is not affected by load changes; in addition, the system always overflows under lower pressure, the energy loss is small, and the energy-saving requirement is met.

Description

Technical Field

[0001] The invention relates to the technical field of hydraulic systems, and in particular to a modular hydraulic energy-saving composite regulating system. Background Art

[0002] The hydraulic control system is the core system of modern mechanical equipment. The host equipment has increasingly higher requirements for the control and regulation performance and energy saving of the hydraulic control system. At present, the three regulation methods of inlet throttling speed regulation, outlet throttling speed regulation and bypass throttling speed regulation are commonly used in hydraulic valve control systems. Although these regulation methods can realize the flow regulation of the hydraulic system, they will lose a lot of energy without exception, causing great waste. At the same time, these will generate a lot of heat, which will increase the temperature of the hydraulic system, accelerate the aging of oil and components, and easily cause leakage, pipeline damage and other faults.

[0003] Specific reasons such as Figure 1 As shown in the figure, in the traditional inlet throttling speed control system, the hydraulic oil from the hydraulic source 01 is output to the hydraulic system 04 through the regulation of the flow control valve 02, and the excess hydraulic oil overflows back to the oil tank at the maximum pressure set by the pressure control valve 03. The hydraulic oil always overflows under high pressure, resulting in large energy loss and high system heat. At the same time, the flow regulation has no constant pressure difference control, the flow regulation has poor rigidity, and is easily affected by load changes.

[0004] Therefore, there is an urgent need in the art for a modular hydraulic energy-saving composite adjustment system to solve the above problems. Summary of the invention

[0005] The purpose of the present invention is to provide a modular hydraulic energy-saving composite regulating system to solve the problems existing in the above-mentioned prior art. A pressure differential regulating valve is added so that the flow of the hydraulic system is controlled by a constant pressure differential, which is not affected by load changes and has good flow regulation rigidity. In addition, the system always overflows at a lower pressure, with less energy loss, and achieves energy saving requirements.

[0006] To achieve the above object, the present invention provides the following solutions:

[0007] The present invention discloses a modular hydraulic energy-saving composite regulating system, comprising a hydraulic pump source, a flow control valve, a pressure control valve, an electromagnetic reversing valve and a pressure differential regulating valve, wherein the hydraulic pump source is connected to the oil inlet of the flow control valve through an oil inlet main pipeline, the oil inlet main pipeline is connected to the pressure control valve through a pressure overflow pipeline, the control port of the pressure control valve is connected to the pressure differential regulating valve through a pressure differential valve oil inlet pipeline, the oil outlet of the pressure differential regulating valve and the oil outlet of the pressure control valve are both connected to an overflow oil tank, the control port of the pressure differential regulating valve and a hydraulic system pipeline are respectively connected to two oil outlets of the flow control valve, the pressure overflow pipeline is connected to the electromagnetic reversing valve through an electromagnetic valve oil inlet pipeline, the electromagnetic reversing valve is connected to the flow control valve through a pipeline, and the electromagnetic reversing valve is used to control the circulation of the flow control valve.

[0008] Preferably, the oil inlet pipeline of the differential pressure valve is connected to the overflow oil tank through a safety overflow pipeline, and a pilot overflow valve is provided on the safety overflow pipeline.

[0009] Preferably, the pressure control valve is a pressure cartridge valve.

[0010] Preferably, the electromagnetic reversing valve is a two-position three-way electromagnetic reversing valve.

[0011] Preferably, the flow control valve is a flow cartridge valve;

[0012] The solenoid valve oil inlet pipeline is connected to the P port of the solenoid reversing valve, the T port of the solenoid reversing valve is connected to the control oil tank through the flow valve oil drain pipeline, and the A port of the solenoid reversing valve is connected to the control port of the flow cartridge valve through the first inlet and outlet oil circuit of the flow valve.

[0013] Preferably, the flow control valve is a proportional flow valve;

[0014] The solenoid valve oil inlet pipeline is connected to the P port of the solenoid reversing valve, the T port of the solenoid reversing valve is connected to the control oil tank through the flow valve oil drain pipeline, the A port of the solenoid reversing valve is connected to the control port of the proportional flow valve through the first inlet and outlet oil circuits of the flow valve, and the B port of the solenoid reversing valve is connected to the working chamber port of the proportional flow valve through the second inlet and outlet oil circuits of the flow valve.

[0015] Compared with the prior art, the present invention has achieved the following technical effects:

[0016] The inlet and outlet pressure difference of the flow control valve of the present invention is controlled by the pressure difference regulating valve and maintained at a substantially constant value, and the flow regulation rigidity is good and is not affected by load changes. The excess flow from the hydraulic pump source overflows back to the oil tank through the pressure control valve at a lower load pressure, and the energy utilization rate is high. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0018] Figure 1 It is a structural diagram of a traditional inlet throttling speed control system;

[0019] Figure 2 This is a structural schematic diagram of a modular hydraulic energy-saving composite adjustment system according to Embodiment 1;

[0020] Figure 3 This is a structural schematic diagram of a modular hydraulic energy-saving composite adjustment system according to Embodiment 2;

[0021] In the figure: 01- hydraulic source; 02- flow control valve; 03- pressure control valve; 04- hydraulic system;

[0022] 1-Hydraulic pump source; 2-Flow control valve; 3-Pressure control valve; 4-Solenoid reversing valve; 5-Pressure differential regulating valve; 6-Pilot relief valve; 7-Overflow oil tank; 8-Control oil tank; 9-Main oil inlet pipeline; 10-Solenoid valve oil inlet pipeline; 11-Pressure overflow pipeline; 12-Flow valve oil drain pipeline; 13-Flow valve first inlet and outlet oil pipeline; 14-Pressure differential valve oil inlet pipeline; 15-Safety overflow pipeline; 16-Pressure differential valve oil drain pipeline; 17-Pressure differential valve control pipeline; 18-Hydraulic system pipeline; 19-Flow valve second inlet and outlet oil pipeline; 20-Pressure valve oil drain pipeline. DETAILED DESCRIPTION

[0023] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0024] The purpose of the present invention is to provide a modular hydraulic energy-saving composite regulating system to solve the problems existing in the above-mentioned prior art. A pressure differential regulating valve is added so that the flow of the hydraulic system is controlled by a constant pressure differential, which is not affected by load changes and has good flow regulation rigidity. In addition, the system always overflows at a lower pressure, with less energy loss, and achieves energy saving requirements.

[0025] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0026] Embodiment 1

[0027] like Figure 2 As shown, this embodiment provides a modular hydraulic energy-saving composite regulation system, including a hydraulic pump source 1, a flow control valve 2, a pressure control valve 3, an electromagnetic reversing valve 4 and a pressure difference regulating valve 5. Among them, the hydraulic pump source 1 is an existing hydraulic station, and the hydraulic pump source 1 is connected to the oil inlet of the flow control valve 2 through an oil inlet main pipeline 9. The main oil inlet pipeline 9 is also connected to the oil inlet of the pressure control valve 3 through the pressure overflow pipeline 11, and the control port of the pressure control valve 3 is connected to the pressure differential regulating valve 5 through the pressure differential valve oil inlet pipeline 14. The pressure differential regulating valve 5 is the prior art, and the oil outlet of the pressure differential regulating valve 5 and the oil outlet of the pressure control valve 3 are both connected to the overflow oil tank 7. Specifically, the oil outlet of the pressure differential regulating valve 5 is connected to the overflow oil tank 7 through the pressure differential valve oil drain pipeline 16, and the oil outlet of the pressure control valve 3 is connected to the overflow oil tank 7 through the pressure valve oil drain pipeline 20, so that the hydraulic oil overflowing in the pressure differential regulating valve 5 and the pressure control valve 3 can eventually flow into the overflow oil tank 7. The control port of the pressure difference regulating valve 5 and the hydraulic system pipeline 18 are respectively connected to the two oil outlets of the flow control valve 2. The pressure overflow pipeline 11 is connected to the electromagnetic reversing valve 4 through the solenoid valve oil inlet pipeline 10. The electromagnetic reversing valve 4 is connected to the flow control valve 2 through the pipeline. The electromagnetic reversing valve 4 is used to control the circulation of the flow control valve 2.

[0028] The modular hydraulic energy-saving composite adjustment system includes standby state and working state in actual use:

[0029] Standby state: The hydraulic oil from the hydraulic pump source 1 enters the oil inlet of the flow control valve 2 and the pressure control valve 3 through the main oil inlet pipeline 9 and the pressure overflow pipeline 11 respectively. At this time, the electromagnetic reversing valve 4 is in a power-off state, and the hydraulic oil enters the control chamber of the flow control valve 2 through the electromagnetic valve oil inlet pipeline 10 and the electromagnetic reversing valve 4. The flow control valve 2 is in a closed state under the action of the spring and the hydraulic oil, so that there is no hydraulic oil output from the oil outlet of the flow control valve 2. The hydraulic oil flowing through the pressure control valve 3 will enter the oil inlet of the differential pressure regulating valve 5. The control chamber of the differential pressure regulating valve 5 is connected to the oil outlet of the flow control valve 2 through the differential pressure valve control pipeline 17. At this time, there is no hydraulic oil in the control chamber of the differential pressure regulating valve 5. The differential pressure regulating valve 5 is fully opened under the action of the hydraulic oil at the oil inlet and is connected to the overflow oil tank 7. At this time, the control chamber of the pressure control valve 3 is connected to the overflow oil tank 7 through the pressure difference regulating valve 5, so that the hydraulic oil in the control chamber of the pressure control valve 3 flows into the overflow oil tank 7. Under the action of the hydraulic oil pressure from the main oil inlet pipeline 9, the pressure control valve 3 opens, and the hydraulic oil returns to the overflow oil tank 7 through the pressure control valve 3, so that the modular hydraulic energy-saving composite regulation is in an unloading state.

[0030] Working state: At this time, the electromagnetic reversing valve 4 is in the energized state, the control chamber of the flow control valve 2 is connected to the control oil tank 8 through the electromagnetic valve, the flow control valve 2 is opened, and hydraulic oil is output from the oil outlet of the flow control valve 2. The pressure difference regulating valve 5 is in a balanced state under the control oil from the oil outlet of the flow control valve 2 and the control oil from the oil inlet of the flow control valve 2, so that the pressure difference between the oil inlet and the oil outlet of the flow control valve 2 remains basically unchanged, the output flow of the flow control valve 2 changes with its opening, and is not affected by the load change, realizing the flow regulation of the hydraulic system, and at the same time, the pressure of the hydraulic system is also maintained at the pressure required by the load, and the excess hydraulic oil from the hydraulic pump source 1 returns to the overflow tank 7 through the pressure control valve 3, that is, the pressure control valve 3 overflows under the load pressure state, rather than overflowing at the highest set pressure, thereby achieving the technical effect of energy saving.

[0031] In this embodiment, the differential pressure valve oil inlet pipeline 14 is connected to the overflow oil tank 7 through the safety overflow pipeline 15, one end of the safety overflow pipeline 15 is connected to the differential pressure valve oil inlet pipeline 14, and the other end is connected to the differential pressure valve oil drain pipeline 16, and a pilot overflow valve 6 is provided on the safety overflow pipeline 15. The working principle is described below in combination with the above-mentioned standby state and working state:

[0032] Standby state: The hydraulic oil of the hydraulic pump source 1 passes through the pressure control valve 3 and enters the oil inlets of the differential pressure regulating valve 5 and the pilot relief valve 6 respectively. Since the pilot relief valve 6 has been set to the maximum working pressure, the pressure limiting valve is in a closed state at this time, so that the hydraulic oil flowing through the pressure control valve 3 can only flow to the differential pressure regulating valve 5. Therefore, the pilot relief valve 6 in the standby state does not actually work, and the working principle of the system is the same as the above-mentioned standby state.

[0033] Working state: Under the above normal conditions, the excess hydraulic oil from the hydraulic pump source 1 returns to the overflow tank 7 through the pressure control valve 3, that is, the pressure control valve 3 overflows under the load pressure state, rather than overflowing under the maximum set pressure, thereby achieving the technical effect of energy saving. However, if the pressure of the hydraulic oil is higher than the maximum set pressure of the pilot overflow valve 6, the pilot overflow valve 6 is opened at this time, the purpose of which is to ensure system safety.

[0034] In this embodiment, the pressure control valve 3 is an existing common pressure cartridge valve. It should be noted that a throttling channel is provided on the valve core of the pressure cartridge valve in this embodiment. When the pressure control valve 3 is not opened, the hydraulic oil from the hydraulic pump source 1 will flow to the pressure differential regulating valve 5 through the throttling channel.

[0035] In this embodiment, the electromagnetic reversing valve 4 is an existing two-position three-way electromagnetic reversing valve 4 .

[0036] In this embodiment, the flow control valve 2 is a flow cartridge valve, and the pilot relief valve 6 is a conventional mechanical relief valve (ie, non-electrically controlled).

[0037] Specifically, the solenoid valve oil inlet pipeline 10 is connected to the P port of the solenoid reversing valve 4, the T port of the solenoid reversing valve 4 is connected to the control oil tank 8 through the flow valve oil drain pipeline 12, the A port of the solenoid reversing valve 4 is connected to the control port of the flow cartridge valve through the first inlet and outlet oil circuit 13 of the flow valve, and the B port of the solenoid reversing valve 4 is not connected.

[0038] When the flow cartridge valve is closed, the state of the solenoid reversing valve 4 is as follows: Figure 2 As shown, the first inlet and outlet oil circuit 13 of the flow valve is connected with the solenoid valve oil inlet pipeline 10 through the solenoid reversing valve 4. At this time, the hydraulic oil in the solenoid valve oil inlet pipeline 10 enters the control chamber of the flow cartridge valve, and squeezes the valve core of the flow cartridge valve downward under the action of the hydraulic oil and the spring, thereby closing the oil outlets on both sides of the flow cartridge valve.

[0039] When the flow cartridge valve needs to be opened, the position of the electromagnetic reversing valve 4 is switched so that the first inlet and outlet oil circuit 13 of the flow valve is connected to the control oil tank 8 through the flow valve oil drain line 12. At this time, the hydraulic oil in the control chamber of the flow cartridge valve flows into the control oil tank 8 through the flow valve oil drain line 12, and the hydraulic oil pressure at the oil inlet is greater than the spring force, thereby pushing the valve core of the flow cartridge valve to move upward, thereby opening the oil outlets on both sides of the flow cartridge valve.

[0040] Embodiment 2

[0041] like Figure 3 As shown, this embodiment provides a modular hydraulic energy-saving composite adjustment system, and the disclosed technical features are basically the same as those disclosed in the first embodiment, except that:

[0042] In this embodiment, the flow control valve 2 is a proportional flow valve, and the pilot relief valve 6 is a conventional electric relief valve (ie, solenoid-controlled).

[0043] The specific connection relationship is that the solenoid valve oil inlet pipeline 10 is connected to the P port of the solenoid reversing valve 4, the T port of the solenoid reversing valve 4 is connected to the control oil tank 8 through the flow valve oil drain pipeline 12, the A port of the solenoid reversing valve 4 is connected to the control port of the proportional flow valve through the first inlet and outlet oil circuit 13 of the flow valve, and the B port of the solenoid reversing valve 4 is connected to the working chamber port of the proportional flow valve through the second inlet and outlet oil circuit 19 of the flow valve.

[0044] When the proportional flow valve is closed, the state of the electromagnetic reversing valve 4 is as follows: Figure 3As shown, the first inlet and outlet oil circuit 13 of the flow valve is connected with the solenoid valve oil inlet pipeline 10 through the solenoid reversing valve 4. At this time, the hydraulic oil in the solenoid valve oil inlet pipeline 10 enters the control chamber of the proportional flow valve, and squeezes the valve core of the proportional flow valve downward under the action of the hydraulic oil and the electromagnet, while the hydraulic oil in the working chamber of the proportional flow valve flows into the control oil tank 8 through the second inlet and outlet oil circuit 19 of the flow valve, thereby closing the oil outlets on both sides of the proportional flow valve.

[0045] When the proportional flow valve needs to be opened, the position of the solenoid reversing valve 4 is switched so that the first inlet and outlet oil circuit 13 of the flow valve is connected to the control oil tank 8 through the flow valve oil drain line 12, and the second inlet and outlet oil circuit 19 of the flow valve is connected to the solenoid valve oil inlet line 10. At this time, the hydraulic oil in the control chamber of the proportional flow valve flows into the control oil tank 8 through the flow valve oil drain line 12, and the hydraulic oil in the solenoid valve oil inlet line 10 flows into the working chamber of the proportional flow valve, so that the hydraulic oil pressure at its oil inlet is greater than the electromagnet force, thereby pushing the valve core of the proportional flow valve to move upward, thereby opening the oil outlets on both sides of the proportional flow valve.

[0046] The present invention uses specific examples to illustrate the principles and implementation methods of the present invention. The above examples are only used to help understand the method and core ideas of the present invention. At the same time, for those skilled in the art, according to the ideas of the present invention, there will be changes in the specific implementation methods and application scope. In summary, the content of this specification should not be understood as limiting the present invention.

Claims

1. A modular hydraulic energy-saving composite adjustment system, characterized in that: It includes a hydraulic pump source, a flow control valve, a pressure control valve, an electromagnetic reversing valve and a pressure differential regulating valve. The hydraulic pump source is connected to the oil inlet of the flow control valve through a main oil inlet pipeline, the main oil inlet pipeline is connected to the pressure control valve through a pressure overflow pipeline, the control port of the pressure control valve is connected to the pressure differential regulating valve through a pressure differential valve oil inlet pipeline, the oil outlet of the pressure differential regulating valve and the oil outlet of the pressure control valve are both connected to an overflow oil tank, the control port of the pressure differential regulating valve and the hydraulic system pipeline are respectively connected to the two oil outlets of the flow control valve, the pressure overflow pipeline is connected to the electromagnetic reversing valve through the electromagnetic valve oil inlet pipeline, the electromagnetic reversing valve is connected to the flow control valve through a pipeline, and the electromagnetic reversing valve is used to control the circulation of the flow control valve.

2. The modular hydraulic energy-saving composite adjustment system according to claim 1 is characterized in that: The oil inlet pipeline of the differential pressure valve is connected with the overflow oil tank through a safety overflow pipeline, and a pilot overflow valve is arranged on the safety overflow pipeline.

3. The modular hydraulic energy-saving composite adjustment system according to claim 1 is characterized in that: The pressure control valve is a pressure cartridge valve.

4. The modular hydraulic energy-saving composite adjustment system according to claim 1 is characterized in that: The electromagnetic reversing valve is a two-position three-way electromagnetic reversing valve.

5. The modular hydraulic energy-saving composite adjustment system according to claim 4 is characterized in that: The flow control valve is a flow cartridge valve; The solenoid valve oil inlet pipeline is connected to the P port of the solenoid reversing valve, the T port of the solenoid reversing valve is connected to the control oil tank through the flow valve oil drain pipeline, and the A port of the solenoid reversing valve is connected to the control port of the flow cartridge valve through the first inlet and outlet oil circuit of the flow valve.

6. The modular hydraulic energy-saving composite adjustment system according to claim 4 is characterized in that: The flow control valve is a proportional flow valve; The solenoid valve oil inlet pipeline is connected to the P port of the solenoid reversing valve, the T port of the solenoid reversing valve is connected to the control oil tank through the flow valve oil drain pipeline, the A port of the solenoid reversing valve is connected to the control port of the proportional flow valve through the first inlet and outlet oil circuits of the flow valve, and the B port of the solenoid reversing valve is connected to the working chamber port of the proportional flow valve through the second inlet and outlet oil circuits of the flow valve.

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