Non-equal-displacement double-variable pump source driving device of winch heave compensation system

Abstract

The utility model discloses a non-equal-displacement double-variable pump source driving device of a winch heave compensation system, which belongs to the technical field of ocean engineering equipment and comprises a frame, an oil tank, an assembly support and a pump source driving pump, and the pump source driving pump is used for providing hydraulic oil power for a winch driving oil cylinder. The pump source driving pump adopts a variable pump with adjustable flow and is driven by a servo motor; the rack is of an upper-layer and lower-layer type, the oil tank is arranged on the upper layer of the rack, the servo motor and the variable pump are arranged on the assembly support, and the assembly support is fixedly connected to the lower layer of the rack through bolts. According to the pump source driving device, the advantage of high response speed of a pump source based on the combination of a small-rotational-inertia motor and a small-displacement variable pump is fully utilized, and the characteristic of wide adjustment range of a pump source based on the combination of a large-rotational-inertia motor and a large-displacement variable pump is combined, so that the system dynamic characteristics of the direct-drive pump source driving device are integrally improved.

Description

Technical Field

[0001] This utility model relates to the field of marine engineering equipment technology, specifically to a non-uniform displacement dual variable pump source drive device for a winch heave compensation system. Background Technology

[0002] Heave-compensated winches are mainly used in offshore floating operations, such as ultra-deep drilling and floating hoisting. The winch's heave compensation function ensures that offshore floating operations are unaffected by waves, guaranteeing stable operation during hoisting work. Compared to electric winches, hydraulic winches have advantages such as smaller size, more compact structure, and higher reliability. Heavy-duty heave-compensated hydraulic winches consume a lot of power; therefore, employing energy recovery technology is one of the effective measures to improve their efficiency and reduce power consumption.

[0003] The heave compensation system in a hydraulic winch is an essential device for ensuring the normal operation of ultra-deep floating drilling platforms in the deep sea. Winch-type heave compensation systems using a direct-drive pump source, where the hydraulic pump is directly driven by an electric motor, offer advantages such as unlimited compensation stroke, high power efficiency, and a low center of gravity. However, they also suffer from drawbacks such as slow response speed and relatively low compensation accuracy. Among these, the response speed of the direct-drive pump source has the greatest impact on the system's compensation performance. Utility Model Content

[0004] The purpose of this invention is to provide a non-uniform displacement dual variable pump source drive device for a winch heave compensation system with fast response speed.

[0005] To solve the above-mentioned technical problems, the technical solution adopted by this utility model is as follows:

[0006] A non-uniform displacement dual variable pump source drive device for a winch heave compensation system includes a frame, an oil tank, an assembly bracket, and a pump source drive pump. The pump source drive pump is used to provide hydraulic power to the winch drive cylinder. The pump source drive pump is characterized by being a variable pump with adjustable flow rate, driven by a servo motor; the frame is a two-layer frame, with the oil tank located on the upper layer, and the servo motor and variable pump mounted on the assembly bracket, which is bolted to the lower layer of the frame.

[0007] Furthermore, the pump source driving pump is provided in multiple ways, which are divided into large displacement pump source driving pump and small displacement pump source driving pump. The large displacement pump source driving pump uses a servo motor with a large moment of inertia to directly drive the large displacement variable pump, and the small displacement pump source driving pump uses a servo motor with a small moment of inertia to directly drive the small displacement variable pump. The large displacement pump source driving pump and the small displacement pump source driving pump are combined to form a non-equal displacement dual variable pump direct drive pump source.

[0008] Furthermore, the oil tank is connected to an oil output main pipe and an oil return main pipe. The oil output main pipe is connected to the oil inlet end of multiple pump source driven pumps through multiple oil input branch pipes. The oil outlet end of the multiple pump source driven pumps is connected to multiple oil output branch pipes. The multiple oil output branch pipes are connected to the oil return main pipe through a winch driven cylinder.

[0009] Furthermore, each of the plurality of oil output branch pipes is equipped with a pressure gauge, which is used to detect the oil pressure inside the oil output branch pipe.

[0010] Furthermore, each of the multiple oil output branch pipes is equipped with an overflow valve.

[0011] Furthermore, there are 5 pump source drive pumps and 5 assembly brackets. The 5 pump source drive pumps are respectively installed on the 5 assembly brackets. Two assembly brackets are installed on the lower surface of the frame along the longitudinal direction and two along the transverse direction, with equal longitudinal gap distance as the positioning dimension. One assembly bracket is installed at the transverse centerline on the lower surface of the frame.

[0012] Furthermore, the oil tank is a rectangular hexahedron, and according to empirical formulas, the capacity of the oil tank is 3-5 times the maximum flow rate of the system to ensure heat dissipation and oil residence time.

[0013] Furthermore, the small displacement variable pump is an axial piston variable pump of model A4CSG750EPG / 30R-VPH85F994N manufactured by Rexroth; the small moment of inertia servo motor is a synchronous servo motor of model MSK100D-0200 manufactured by Rexroth.

[0014] Furthermore, the large displacement variable pump is a Rexroth A6V2000EPG12FZ2 piston variable pump; the large moment of inertia servo motor is a SIEMENS 1FT7138-5SB71-7CA1-Z permanent magnet synchronous servo motor.

[0015] The beneficial effects of this utility model are as follows:

[0016] This application proposes a non-uniform displacement dual direct-drive pump source system strategy for the heave compensation system. It uses servo motors with different moments of inertia paired with variable pumps with different displacements to form a direct-drive pump source control system with non-uniform displacement dual direct-drive pump sources. This fully utilizes the advantage of fast pump source response speed based on the combination of small moment of inertia motors and small displacement variable pumps, and combines the wide adjustment range of pump sources based on large moment of inertia motors and large displacement variable pumps, thereby improving the overall dynamic characteristics of the direct-drive pump source drive device. Attached Figure Description

[0017] The present invention will be further described with reference to the accompanying drawings, but the embodiments in the drawings do not constitute any limitation on the present invention. For those skilled in the art, other drawings can be obtained based on the following drawings without creative effort:

[0018] Figure 1 This is a schematic diagram of the structure of this utility model;

[0019] Figure 2 for Figure 1 The diagram shows the arrangement of the pump source-driven pump on the lower layer of the frame.

[0020] Figure 3 for Figure 2 The diagram shows the oil circuit schematic of the pump source driving the pump.

[0021] In the diagram: 1. Frame; 2. Oil tank; 3. Assembly bracket; 4. Pump source drive pump; 5. Servo motor; 6. Variable pump; 7. Coupling; 8. Oil output main pipe; 9. Oil return main pipe; 10. Oil input branch pipe; 11. Oil output branch pipe; 12. Pressure gauge; 13. Relief valve. Detailed Implementation

[0022] To enable those skilled in the art to better understand the technical solution of this utility model, the present utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of this application can be combined with each other.

[0023] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper surface", "lower surface", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "forward", "reverse", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0024] like Figure 1 , 2As shown in Figure 3, a non-uniform displacement dual variable pump source drive device for a winch heave compensation system includes a frame 1, an oil tank 2, an assembly bracket 3, and a pump source drive pump 4. The pump source drive pump 4 provides hydraulic power to the winch drive cylinder. The pump source drive pump 4 includes a servo motor 5 and a variable pump 6, where the flow rate of the pump 6 is adjustable. The servo motor 5 is connected to the frame 1 via a coupling 7. The frame 1 adopts a two-layer frame structure, with the oil tank 2 located on the upper layer and the servo motor 5 and variable pump 6 mounted on the assembly bracket 3. The assembly bracket 3 is bolted to the lower layer of the frame 1. During maintenance, it is only necessary to push the assembly bracket containing the faulty component out of the lower layer of the frame for repair and replacement, making maintenance convenient. The vertical installation structure effectively reduces the deck area occupied by the overall direct-drive pump source drive device, and the layered structure allows for the regular installation of each component, resulting in a compact and orderly structure.

[0025] The pump source driving pump 4 is provided in multiple units, which are divided into large-displacement pump source driving pumps and small-displacement pump source driving pumps. The large-displacement pump source driving pump uses a servo motor with a large moment of inertia to directly drive the large-displacement variable pump, and the small-displacement pump source driving pump uses a servo motor with a small moment of inertia to directly drive the small-displacement variable pump. The large-displacement pump source driving pump and the small-displacement pump source driving pump are combined to form a non-equal displacement dual variable pump direct drive pump source. In this embodiment, there are 5 pump source driving pumps and 5 mounting brackets. The 5 pump source driving pumps are respectively mounted on 5 mounting brackets. Two mounting brackets are installed on the lower surface of the frame along the longitudinal direction and two along the transverse direction, with equal longitudinal gap distance as the positioning dimension. One mounting bracket is installed at the transverse centerline on the lower surface of the frame.

[0026] Based on the design criteria and system flow and pressure requirements, a Rexroth A4CSG750EPG / 30R-VPH85F994N axial piston variable pump was selected for the small displacement variable pump. It has a nominal pressure of 350 bar, a maximum pressure of 400 bar, a maximum displacement of 750 ml / r, a maximum speed of 1600 r / min, a maximum allowable flow rate of 1200 L / min, and a rotational inertia of 0.0116 kg·m². Considering the system requirements and the structural requirements of the selected variable pump, a Rexroth MSK100D-0200 synchronous servo motor with a small rotational inertia was selected. It has a maximum allowable speed of 2000 r / min and a rotational inertia of 0.0045 kg·m².

[0027] In the selection of pump source for the large displacement variable pump combination, the large displacement variable pump is a Rexroth A6V2000EPG12FZ2 piston variable pump with a nominal pressure of 315 bar, a maximum pressure of 350 bar, a maximum displacement of 2000 ml / r, a maximum speed of 650 r / min, a maximum allowable flow rate of 1300 L / min, and a rotational inertia of 0.256 kg·m2. The large rotational inertia servo motor is a SIEMENS 1FT7138-5SB71-7CA1-Z permanent magnet synchronous servo motor with a rated speed of 1500 r / min, a maximum allowable speed of 3600 r / min, and a rotational inertia of 0.0896 kg·m2.

[0028] The oil tank 2 is connected to an oil output main pipe 8 and an oil return main pipe 9. The oil output main pipe 8 is connected to the oil inlet end of multiple pump source driven pumps 4 through multiple oil input branch pipes 10. The oil outlet end of the multiple pump source driven pumps 4 is connected to multiple oil output branch pipes 11. The multiple oil output branch pipes 11 are connected to the oil return main pipe 9 through a winch driven cylinder. Each of the multiple oil output branch pipes 11 is equipped with a pressure gauge 12, which is used to detect the oil pressure in the pipe of the oil output branch pipe. Each of the multiple oil output branch pipes 11 is also equipped with an overflow valve 13.

[0029] Oil tank 2 is a rectangular hexahedron. Based on empirical formulas, its capacity is calculated to be 3-5 times the system's maximum flow rate to ensure adequate heat dissipation and oil residence time. Considering this and limited space, the oil tank of this device is designed to be 3 times the system's maximum flow rate, with dimensions of 3×2.5×2.4m, a capacity of 18000L, and a wall thickness of 100mm. The tank contains both suction and return pipes, positioned below the lowest oil level to prevent air suction and air bubbles from splashing during return. The suction pipe is equipped with a filter to remove impurities from the oil, improving the service life of hydraulic components. The return pipe is angled at 45° towards the inner wall of the tank to increase the oil outlet area, effectively preventing return oil from impacting bottom deposits and causing wear on the tank, while also facilitating heat dissipation.

[0030] The pump source drive device of this application has the characteristics of simple and compact structure, small space occupation, convenient maintenance, energy saving and environmental protection, fast dynamic response speed of pump source, wide adjustment range, complete functions and strong practicality.

[0031] Working Principle: To improve the response speed of the direct-drive pump source, a dual-variable direct-drive pump source with a servo motor driving a variable pump can be used. Adjusting the displacement of both the servo motor and the variable pump simultaneously can enhance the response speed. However, due to power limitations of individual servo motors and pumps, heavy-duty heave compensation systems suitable for deep-sea operations require multiple dual-variable direct-drive pump sources. The greater the power of the direct-drive pump source, the larger the pump displacement, and the greater the moment of inertia. A greater moment of inertia results in a slower response speed. Considering that the frequency of heave motion of the work platform caused by waves varies during actual operation—higher frequencies result in smaller amplitudes and lower speeds, requiring less flow for compensation; lower frequencies result in larger amplitudes and faster speeds, requiring more flow for compensation—multiple direct-drive pump sources can utilize variable pumps with different displacements.

[0032] Furthermore, those skilled in the art can combine and integrate the different embodiments or examples described herein, as well as the features of those different embodiments or examples, without contradiction. Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present invention.

Claims

1. A non-uniform displacement dual-variable pump source drive device for a winch heave compensation system, comprising a frame, an oil tank, an assembly bracket, and a pump source drive pump, wherein the pump source drive pump is used to provide hydraulic power to the winch drive cylinder, characterized in that: The pump source driving pump is a variable pump with adjustable flow rate, driven by a servo motor; the frame adopts a two-layer frame, the oil tank is located on the upper layer of the frame, the servo motor and variable pump are located on the mounting bracket, and the mounting bracket is fixed to the lower layer of the frame by bolts.

2. The non-uniform displacement dual variable pump source drive device for a winch heave compensation system according to claim 1, characterized in that: The pump source drive pump is provided in multiple ways, and the multiple pump source drive pumps are divided into large displacement pump source drive pumps and small displacement pump source drive pumps. The large displacement pump source drive pump uses a servo motor with a large rotational inertia to directly drive the large displacement variable pump, and the small displacement pump source drive pump uses a servo motor with a small rotational inertia to directly drive the small displacement variable pump. The large displacement pump source drive pump and the small displacement pump source drive pump are combined to form a non-equal displacement dual variable pump direct drive pump source.

3. The non-uniform displacement dual variable pump source drive device for a winch heave compensation system according to claim 2, characterized in that: The oil tank is connected to an oil output main pipe and an oil return main pipe. The oil output main pipe is connected to the oil inlet end of multiple pumps driven by multiple pumps through multiple oil input branch pipes. The oil outlet end of the multiple pumps driven by multiple pumps is connected to multiple oil output branch pipes. The multiple oil output branch pipes are connected to the oil return main pipe through a winch-driven cylinder.

4. The non-uniform displacement dual variable pump source drive device for a winch heave compensation system according to claim 3, characterized in that: Each of the multiple oil output branch pipes is equipped with a pressure gauge, which is used to detect the oil pressure inside the oil output branch pipe.

5. The non-uniform displacement dual variable pump source drive device for a winch heave compensation system according to claim 4, characterized in that: Each of the multiple oil output branch pipes is equipped with an overflow valve.

6. The non-uniform displacement dual variable pump source drive device for a winch heave compensation system according to claim 5, characterized in that: The pump source drives five pumps, and the assembly brackets are provided. The five pump source drives are respectively installed on the five assembly brackets. Two assembly brackets are installed on the lower surface of the frame along the longitudinal direction and two along the transverse direction, with equal longitudinal gap distance as the positioning dimension. One assembly bracket is installed at the transverse centerline on the lower surface of the frame.

7. The non-uniform displacement dual variable pump source drive device for a winch heave compensation system according to claim 6, characterized in that: The oil tank is a rectangular hexahedron with a capacity of 3-5 times the system's maximum flow rate to ensure heat dissipation and oil residence time.

8. The non-uniform displacement dual variable pump source drive device for a winch heave compensation system according to claim 7, characterized in that: The small displacement variable pump is an axial piston variable pump of model A4CSG750EPG / 30R-VPH85F994N manufactured by Rexroth; the small moment of inertia servo motor is a synchronous servo motor of model MSK100D-0200 manufactured by Rexroth.

9. The non-uniform displacement dual variable pump source drive device for a winch heave compensation system according to claim 8, characterized in that: The large displacement variable pump is a Rexroth A6V2000EPG12FZ2 piston variable pump; the large moment of inertia servo motor is a SIEMENS 1FT7138-5SB71-7CA1-Z permanent magnet synchronous servo motor.

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