Energy-saving fluid motor resistant to high pressure and pressure pulsation

Abstract

The utility model discloses an energy-saving fluid motor resistant to high pressure and pressure pulsation, and relates to the technical field of hydraulic motors, the energy-saving fluid motor comprises a motor body, cup-shaped blades, an output wheel shaft and a shock wave recoverer; the periphery of the output wheel shaft is connected with a plurality of cup-shaped blades; the motor body is further provided with an oil inlet channel, an oil outlet channel and a shock wave channel. The large pulse flows through a shock wave recoverer at the bottom of the shock wave channel, is boosted and stabilized and then enters a flow-aiding channel and a braking channel on the two sides; a flow-aiding control valve is connected in the flow-aiding channel, and a brake control valve is connected in the brake channel; when the flow-aiding control valve is opened, the cup-shaped blade drives the output wheel shaft to rotate under the impact of incoming flow in the oil inlet channel and the flow-aiding channel; when the brake control valve is opened, the brake channel conveys the pulsating flow subjected to pressure boosting and pressure stabilizing into the cup-shaped blades, rotation of the cup-shaped blades is hindered, and the output wheel shaft can achieve flexible semi-brake under the action of opposite torque.

Description

Technical Field

[0001] This application belongs to the field of hydraulic motor technology, specifically relating to an energy-saving fluid motor that can withstand high pressure and pressure pulsation. Background Technology

[0002] A hydraulic motor, also known as a hydraulic starter or hydraulic starter, works by using a liquid as the working medium and transferring energy through fluid transmission, utilizing the kinetic energy of the liquid rather than the pressure difference energy of hydraulic pressure. Hydraulic motors generally require forward and reverse rotation, so their internal structure should be symmetrical. However, large mixers are typically driven in one direction only, requiring speeds below 500 rpm, necessitating low-speed hydraulic motors that do not require forward or reverse rotation.

[0003] The main characteristics of existing low-speed hydraulic motors are large displacement, large size, and low speed. Therefore, they can be directly connected to the transmission mechanism without the need for a reduction gear, simplifying the transmission mechanism. In contrast, conventional vane hydraulic motors require springs installed at the root of the vanes to ensure that the vanes remain in close contact with the inner surface of the stator. The vanes rely on high-speed rotation together with the rotor to keep them in close contact with the inner surface of the stator, acting as an oil seal and forming a working volume so that the motor can start normally.

[0004] Hydraulic motors must have a large starting torque. Starting torque refers to the torque that the motor shaft can output when starting from a standstill. This torque is typically greater than the torque during operation under the same operating pressure differential. Therefore, to make the starting torque as close as possible to the torque during operation, the motor's torque pulsation and internal friction must be minimal. Furthermore, to provide overload protection, a safety valve needs to be installed near the hydraulic motor.

[0005] Currently, there are no commercially available low-speed, stable-torque hydraulic motors that combine the momentum (flow velocity V) and pressure difference energy (ΔP) of a fluid. Therefore, they cannot be directly applied to discrete flow transmission and control systems in quasi-rigid hydraulic pipelines. This is because the quasi-rigidity of such systems requires high hydraulic energy within the pipeline, such as greater than 10 MPa. High-speed transmission also involves high-speed pulsating shock waves. If this energy is converted back into high-flow-rate, high-speed fluid kinetic energy and then used by a conventional hydraulic motor, the conversion losses may outweigh the initial goals of energy saving and increased transmission speed in long-distance hydraulic pipelines. Furthermore, directly connecting the energy transmitted through such pipelines to a hydraulic motor would cause instability due to the large and numerous pulsations in the incoming pipeline, making it difficult to control the output speed and torque. Moreover, the safety valve installed at the motor's front end for overload protection would frequently open due to the impact of pulsating shock waves, resulting in energy leakage.

[0006] Therefore, there is an urgent need for an energy-efficient fluid motor that can withstand high pressure and pressure pulsation. Utility Model Content

[0007] This application provides an energy-saving fluid motor that can withstand high pressure and pressure pulsation, in order to solve at least one of the above-mentioned technical problems.

[0008] The technical solution adopted in this application is as follows:

[0009] An energy-saving fluid motor resistant to high pressure and pressure pulsation includes a motor body, cup-shaped blades, an output shaft, and a shock wave recoverer. Multiple cup-shaped blades are connected to the outer periphery of the output shaft. The motor body includes a symmetrically connected motor cover and motor base, with accommodating cavities within the cover and base to house the cup-shaped blades and output shaft. The output shaft transmits power outwards via bearings on the cover and base. The motor body also has an oil inlet and an oil outlet. The axis of the oil inlet is tangent to the rotation trajectory centerline of the cup-shaped blades. At the tangent point, the cup opening of the cup-shaped blades faces the oil inlet. A shock wave channel is positioned perpendicular to the axis of the oil inlet or within a 120° angle range. A one-way valve is installed on the shock wave channel to ensure that the shock wave reaches the shock wave recoverer at the bottom of the channel in a single direction.

[0010] The bottom of the shock channel is connected to a flow aid channel and a braking channel on both sides respectively; the outlet of the flow aid channel is opposite to or perpendicular to the cup mouth of the cup-shaped blade, and the outlet of the braking channel is opposite to or perpendicular to the cup bottom of the cup-shaped blade, so as to ensure that the liquid flow inside is consistent with the rotation direction of the cup-shaped blade or hits the top; a flow aid control valve is connected in the flow aid channel, and a braking control valve is connected in the braking channel.

[0011] After being shocked and pressurized by the shock wave recoverer at the bottom of the shock wave channel, the large pulsating flow enters the flow aid channel and braking channel on both sides. When the flow aid control valve is opened, the cup-shaped vane drives the output wheel shaft to rotate under the impact of the incoming flow in the oil inlet and the flow aid channel. When the braking control valve is opened, the braking channel sends the pressurized and stabilized pulsating flow into the cup-shaped vane, which hinders the rotation of the cup-shaped vane, so that the output wheel shaft can achieve flexible semi-braking under the action of opposite torque.

[0012] Under normal operating conditions, the flow-aiding control valve is normally open and the braking control valve is closed. The cup-shaped blades drive the output wheel shaft to rotate under the impact of the incoming flow in the oil inlet. The incoming flow in the oil inlet, including the shock wave pulsation part, is pressurized after the shock wave recoverer in the shock wave channel absorbs the pulsation energy. The hydraulic pressure is stabilized and flows to the flow-aiding channel, and then to the cup-shaped blades opposite the oil inlet. The shock wave recovery energy assists the impeller to rotate, giving the output wheel shaft an additional positive torque. Under braking conditions, the flow-aiding control valve is normally open and the braking control valve is open. The braking channel sends the hydraulic flow recovered from the shock wave to the cup-shaped blades opposite the oil outlet, hindering the rotation of the cup-shaped blades, so that the output wheel shaft can be flexibly braked under the action of opposite torque.

[0013] The axis of the oil outlet passage is tangent to the center line of the rotation trajectory of the cup-shaped blade, and the bottom of the cup-shaped blade at the tangency point is directly opposite the oil outlet passage; the center lines of the oil outlet passage and the oil inlet passage are collinear or not collinear; at least 3 cup-shaped blades can be retained in the accommodating cavity between the oil outlet passage and the oil inlet passage to ensure smooth torque and full energy utilization; when the center lines of the oil outlet passage and the oil inlet passage are collinear, the oil outlet passage and the accommodating cavity can adopt a snail shell structure.

[0014] The angle between the flow aid channel and the oil inlet channel is less than 90°; or the angle between the brake channel and the oil outlet channel is greater than 90°. When the flow aid control valve is open, the pressure fluid in the flow aid channel assists the oil inlet channel in increasing the rotational energy input to the cup-shaped blades. When the brake control valve is open and the flow aid control valve is closed, the pressure fluid in the brake channel hinders the outflow from the oil outlet channel or hinders the rotation of the cup-shaped blades.

[0015] The output shaft includes an output shaft body and an output shaft; the output shaft body is connected to the motor body; the output shaft body includes a wheel and a rotating shaft, the wheel has multiple cup-shaped blades circumferentially connected, the rotating shaft is fixedly connected to the wheel, and both ends of the rotating shaft are connected to the bearing end caps in the bearing support holes inside the motor body through dynamic seals; the output shaft passes through the bearing end caps and the rotating shaft, and the output shaft is fixedly connected to the rotating shaft through a key or spline.

[0016] The cup-shaped blade includes a cup-shaped blade body and a connector; the cup-shaped blade body adopts a gourd-shaped, hemispherical, or multi-arc structure; the connector protrudes and connects to one side of the cup-shaped blade body; multiple insertion slots for inserting the connector are opened circumferentially on the circumferential end face of the turntable; the connector is connected to the insertion locking device on both sides along the axial direction, and the insertion locking device limits the connector in the axial direction, so that the connector is locked and connected to the turntable, and the cup-shaped blade is connected to the circumference of the turntable.

[0017] The connector has a ring-shaped main body and an arc-shaped connecting segment connected to the main body; one end of the connecting segment is tangentially connected to the outer periphery of the main body, and the other end of the connecting segment is tangentially connected to the cup-shaped blade.

[0018] The braking channel includes a first fluid section and a second fluid section; the first fluid section is connected to the second fluid section, the first fluid section is connected to the recovery channel, and the second fluid section is connected to the accommodating cavity or the oil outlet channel.

[0019] The first fluid section is vertically connected to the shock channel; or, the first fluid section is inclinedly connected to the shock channel.

[0020] The flow channel includes a third fluid section and a fourth fluid section; the third fluid section is connected to the fourth fluid section, the third fluid section is connected to the shock wave channel, and the fourth fluid section is connected to the accommodating cavity or the oil inlet channel.

[0021] An energy-saving fluid motor that can withstand high pressure and pressure pulsation also includes a sensor, which is disposed outside the motor cover and / or motor base outside the cavity accommodating the rotating cup-shaped blades of the motor body.

[0022] The outlet flow rate V of the oil passage is measured by a sensor. 1i The time T required for outflow 1i The number n of cup-shaped blades passing through 1i The average time t between two adjacent cup-shaped blades 1i Through the formula:

[0023] q 1i =Q 1i / (n 1i ×t 1i )=(V 1i / T 1i ) / (n 1i ×t 1i )

[0024] In the formula, Q 1i This represents the flow rate through the cup-shaped blades each time.

[0025] The displacement q of each passage through the cup-shaped blades can be obtained. 1i The average displacement q of the motor is obtained by averaging the displacement measurements from each measurement.

[0026] q=(q 11 +q 12+...+ q 1i ) / i

[0027] In the formula, q is the average displacement of the motor, q 11 For the first displacement through the cup-shaped blades, q 12 For the second passage through the cup-shaped blades, q 1i Let i be the displacement of the i-th time through the cup-shaped blade, where i ≥ 3.

[0028] Due to the adoption of the above technical solution, the beneficial effects achieved by this application are as follows:

[0029] 1. An energy-saving fluid motor resistant to high pressure and pressure pulsation, comprising a motor body, cup-shaped blades, an output shaft, and a shock wave recoverer; multiple cup-shaped blades are connected to the outer periphery of the output shaft; the motor body includes a symmetrically connected motor cover and a motor seat, with accommodating cavities formed within the motor cover and motor seat to accommodate the cup-shaped blades and the output shaft, and the output shaft transmitting power outward through bearings on the motor cover and motor seat; the motor body also has an oil inlet passage and an oil outlet passage, the axis of the oil inlet passage being tangent to the center line of the rotation trajectory of the cup-shaped blades, the cup opening of the cup-shaped blades at the tangent point facing the oil inlet passage, and a shock wave channel being provided within a range perpendicular to or at an angle of 120° to the axis of the oil inlet passage; a one-way valve is provided on the shock wave channel to ensure that the shock wave reaches the shock wave recoverer at the bottom of the shock wave channel in a single direction;

[0030] Under normal operating conditions, the flow-aiding control valve is normally open and the braking control valve is closed. The cup-shaped blades drive the output wheel shaft to rotate under the impact of the incoming flow in the oil inlet. The incoming flow in the oil inlet, including the shock wave pulsation part, is pressurized after the shock wave recoverer in the shock wave channel absorbs the pulsation energy. The hydraulic pressure is stabilized and flows to the flow-aiding channel, and then to the cup-shaped blades opposite the oil inlet. The shock wave recovery energy assists the impeller to rotate, giving the output wheel shaft an additional positive torque. Under braking conditions, the flow-aiding control valve is normally open and the braking control valve is open. The braking channel sends the hydraulic flow recovered from the shock wave to the cup-shaped blades opposite the oil outlet, hindering the rotation of the cup-shaped blades, so that the output wheel shaft can be flexibly braked under the action of opposite torque.

[0031] This application utilizes the absorption and reuse of pulsating energy from the shock channel. There is no need to install a safety valve with overload protection at the front end of the motor. Instead, the shock wave recoverer at the bottom of the shock channel recovers and converts the pulsating shock wave energy, thereby eliminating the waste of pulsating impact energy caused by the safety valve. This fully utilizes the energy transmission and overcomes unnecessary energy loss. Furthermore, by setting up a flow-aiding channel to reuse the recovered and converted pulsating shock wave energy, it also ensures an increase in the motor's output torque and improved operational stability.

[0032] 2. In a preferred embodiment of this application, the output shaft includes an output shaft body and an output shaft; the output shaft body is connected to the motor body; the output shaft body includes a wheel and a rotating shaft, the wheel is circumferentially connected with a plurality of cup-shaped blades, the rotating shaft is connected to the wheel, and both ends of the rotating shaft are respectively connected to the bearing end caps in the bearing support holes in the motor body through dynamic seals; the output shaft passes through the bearing end caps and the rotating shaft, and the output shaft is fixedly connected to the rotating shaft through a key or spline.

[0033] Both ends of the rotary shaft are connected to bearing end covers in the bearing support holes inside the motor body via dynamic seals. The output shaft is independent of the dynamic seals, thus reducing sealing leakage during output shaft movement. The output shaft is independent of the motor body; the bearing end covers and rotary shaft are hollow, and the hollow part of the rotary shaft is equipped with splines or keyways for fixed connection with the output shaft. This allows for easy repositioning of the output shaft, facilitating both motor rotation direction and installation on-site.

[0034] 3. In a preferred embodiment of this application, the flow aid channel can be connected to the oil inlet channel at an angle of less than 90°, or the braking channel can be connected to the oil outlet channel at an angle of greater than 90°. When the flow aid control valve is open, the pressure fluid in the flow aid channel assists the oil inlet channel in increasing the rotational energy input to the cup-shaped blade. When the braking control valve is open and the flow aid control valve is closed, the pressure fluid in the braking channel hinders the outflow from the oil outlet channel or hinders the rotation of the cup-shaped blade.

[0035] When the flow-aiding control valve and the braking control valve are opened simultaneously, the cup-shaped vanes drive the output wheel shaft to rotate under the impingement of the shock wave pulsation flow and differential pressure flow from the oil inlet. After the shock wave pulsation flow is absorbed by the shock wave recoverer in the shock wave channel, the hydraulic flow with stable pressure is released into the flow-aiding channel and the braking channel. The hydraulic flow entering the braking channel hinders the rotation of the cup-shaped vanes, thereby offsetting the positive torque added to the output wheel shaft by the hydraulic flow in the flow-aiding channel. At this time, the flow-aiding control valve is closed while the braking control valve remains open. The positive torque added to the output wheel shaft by the hydraulic flow in the flow-aiding channel disappears, leaving only the hydraulic flow in the braking channel to hinder the rotation of the cup-shaped vanes. This is used to balance or resist the positive torque added to the cup-shaped vanes by the oil inlet, hindering the impeller rotation, thereby enabling the output wheel shaft to achieve flexible semi-braking.

[0036] 4. In a preferred embodiment of this application, the wheel is provided with a plurality of insertion slots and insertion locking devices along its circumference for inserting and connecting cup-shaped blades. The number of cup-shaped blades evenly distributed around the circumference of the wheel can be selected in various ways, but preferably, the number n of cup-shaped blades filling all the insertion slots is preferred. 1i As a standard specification, the number of other evenly distributed cup-shaped blades is n. ji However, j cannot be less than 3, to facilitate the uniform increase of n in the number of blades. 1i Used to change displacement q 1i Increase torque N = ΔP × q 1i ΔP is the pressure difference of the liquid.

[0037] 5. At least three cup-shaped blades can be retained in the accommodating cavity between the oil outlet and the oil inlet to ensure smooth torque and full energy utilization; and when the center lines of the oil outlet and the oil inlet are collinear, the oil outlet and the accommodating cavity can adopt a snail shell structure; which can more effectively utilize all the energy of the impact fluid.

[0038] 6. The wheel can be configured with a spoke structure for large motor drives to reduce the motor's starting inertia and increase its starting torque. A maintenance window is provided on the outer side of the motor cover and / or motor base, which contains a cavity for accommodating the cup-shaped blades. This allows for timely shutdown when a sensor detects a damaged cup-shaped blade, enabling inspection, replacement, or tightening of the damaged blade. Furthermore, the bearing cover, located at the rotating shaft, is relatively far from the cavity for the cup-shaped blades. Therefore, the linear velocity of the dynamic seal contact lip at the rotating shaft is low, resulting in a longer lifespan for the dynamic seal. The connection between the motor cover and / or motor base, separated from the main motor unit, uses a reliable static seal, effectively improving seal life and extending the motor's service life. Attached Figure Description

[0039] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings:

[0040] Figure 1 This is a schematic diagram of the structure of an energy-saving fluid motor that can withstand high pressure and pressure pulsation according to one embodiment of this application;

[0041] Figure 2 This is a schematic diagram of the output shaft of an energy-saving fluid motor that can withstand high pressure and pressure pulsation according to one embodiment of this application;

[0042] In the picture,

[0043] 1. Motor body; 2. Cup-shaped blade; 21. Cup-shaped blade body; 22. Connecting component; 3. Output wheel shaft; 31. Output wheel shaft body; 311. Wheel disc; 312. Rotary shaft; 32. Output shaft; 4. Oil inlet passage; 5. Oil outlet passage; 6. Shock wave channel; 7. Check valve; 8. Braking channel; 81. First fluid section; 82. Second fluid section; 9. Flow aid channel; 91. Third fluid section; 92. Fourth fluid section; 10. Flow aid control valve; 11. Braking control valve; 12. Shock wave recovery device. Detailed Implementation

[0044] To more clearly illustrate the overall concept of this application, a detailed explanation is provided below with reference to the accompanying drawings.

[0045] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, this application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.

[0046] Furthermore, it should be understood in the description of this application that the terms "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not 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.

[0047] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0048] In this application, unless otherwise expressly specified and limited, the "above" or "below" of the second feature can mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium. In the description of this specification, references to terms such as "implementation," "example," "a particular embodiment," "example," or "specific example," etc., indicate that the specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described can be combined in any suitable manner in one or more embodiments or examples.

[0049] This application relates to an energy-saving fluid motor that can withstand high pressure and pressure pulsation, such as... Figure 1-2 As shown, the device includes a motor body 1, cup-shaped blades 2, an output shaft 3, and a shock wave recovery device 12. Multiple cup-shaped blades 2 are connected to the outer periphery of the output shaft 3. The motor body 1 includes a symmetrically connected motor cover and motor seat. The motor cover and motor seat form accommodating cavities for accommodating the cup-shaped blades 2 and the output shaft 3. The output shaft 3 transmits power outwards through bearings on the motor cover and motor seat. The motor body 1 also has an oil inlet channel 4 and an oil outlet channel 5. The axis of the oil inlet channel 4 is tangent to the rotation trajectory centerline of the cup-shaped blades 2. At the tangent point, the cup opening of the cup-shaped blades 2 faces the oil inlet channel 4. A shock wave channel 6 is provided within a range perpendicular to or at an angle of 120° to the axis of the oil inlet channel 4. A one-way valve 7 is provided on the shock wave channel 6 to ensure that the shock wave reaches the shock wave recovery device 12 at the bottom of the shock wave channel 6 in a single direction.

[0050] The bottom of the shock channel 6 is connected to the flow aid channel 9 and the braking channel 8 on both sides respectively; the outlet of the flow aid channel 9 is opposite to or perpendicular to the cup mouth of the cup-shaped blade 2, and the outlet of the braking channel 8 is opposite to or perpendicular to the cup bottom of the cup-shaped blade 2, so as to ensure that the liquid flow inside is consistent with the rotation direction of the cup-shaped blade 2 or hits the top; the flow aid channel 9 is connected to the flow aid control valve 10, and the braking channel 8 is connected to the braking control valve 11.

[0051] After being shocked and stabilized by the shock wave recoverer 12 at the bottom of the shock wave channel, the large pulsating flow enters the flow aid channel 9 and the braking channel 8 on both sides. When the flow aid control valve 10 is opened, the cup-shaped blades drive the output wheel shaft to rotate under the impact of the incoming flow in the oil inlet and the flow aid channel. When the braking control valve 11 is opened, the braking channel 8 sends the pulsating flow after being shocked and stabilized to the cup-shaped blades 2, which hinders the rotation of the cup-shaped blades 2, so that the output wheel shaft 3 can achieve flexible semi-braking under the action of opposite torque.

[0052] Under normal operating conditions, the flow-aiding control valve 10 is normally open and the braking control valve 11 is closed. The cup-shaped blade 2 drives the output wheel shaft 3 to rotate under the impact of the incoming flow in the oil inlet channel 4. The incoming flow in the oil inlet channel 4, including the shock wave pulsation part, is pressurized after the shock wave recoverer 12 of the shock wave channel 6 absorbs the pulsation energy. The hydraulic pressure is stabilized and flows to the flow-aiding channel 9, and then to the cup-shaped blade 2 opposite to the oil inlet channel 4. The shock wave recovery energy assists the impeller to rotate, giving the output wheel shaft 3 an additional positive torque. Under braking conditions, the flow-aiding control valve 10 is normally open and the braking control valve 11 is open. The braking channel 8 sends the hydraulic pressure recovered by the shock wave to the cup-shaped blade 2 opposite to the oil outlet channel 5, which hinders the rotation of the cup-shaped blade 2, so that the output wheel shaft 3 can be flexibly braked under the action of opposite torque.

[0053] Specifically, under normal operating conditions, the flow-aiding control valve 10 is normally open and the braking control valve 11 is closed. The cup-shaped blade 2 drives the output wheel shaft 3 to rotate under the impact of the incoming flow in the oil inlet channel 4. The incoming flow in the oil inlet channel 4, including the shock wave pulsation portion, is pressurized after the shock wave recoverer 12 in the shock wave channel 6 absorbs the pulsation energy. The hydraulic pressure is stabilized and flows to the flow-aiding channel 9, and then reaches the cup-shaped blade 2 opposite to the oil inlet channel 4. The shock wave recovery energy assists the impeller to rotate, giving the output wheel shaft 3 an additional positive torque. Under braking operating conditions, the flow-aiding control valve 10 is normally open and the braking control valve 11 is open. The cup-shaped blade 2 drives the output wheel shaft 3 to rotate under the impact of the incoming flow in the oil inlet channel 4. The blade 2 drives the output wheel shaft 3 to rotate under the impact of the incoming flow in the oil inlet channel 4. The incoming flow in the oil inlet channel 4 includes a shock wave pulsation part. After the shock wave recoverer 12 in the shock wave channel 6 absorbs the pulsation energy, it is pressurized and the hydraulic pressure is stabilized and flows to the flow aid channel 9, and then to the cup-shaped blade 2 opposite to the oil inlet channel 4. The shock wave recovery energy helps the impeller rotate and gives the output wheel shaft 3 an additional positive torque. Meanwhile, the braking channel 8 sends the hydraulic flow recovered by the shock wave to the cup-shaped blade 2 opposite to the oil outlet channel 5, which hinders the rotation of the cup-shaped blade 2, so that the output wheel shaft 3 can be flexibly braked under the action of opposite torque.

[0054] When the flow-aiding control valve 10 and the braking control valve 11 are opened simultaneously, the cup-shaped vane 2 is driven by the shock wave pulsating flow and differential pressure flow from the oil inlet 4 to rotate the output wheel shaft 3. After the shock wave pulsating flow is absorbed by the shock wave recoverer 12 in the shock wave channel 6, the hydraulic flow with stable pressure is released into the flow-aiding channel 9 and the braking channel 8. The hydraulic flow entering the braking channel 8 hinders the rotation of the cup-shaped vane 2, thereby offsetting the positive torque added to the output wheel shaft 3 by the hydraulic flow in the flow-aiding channel 9. At this time, the flow-aiding control valve 10 is closed while the braking control valve 11 is kept open. The positive torque added to the output wheel shaft 3 by the hydraulic flow in the flow-aiding channel 9 disappears, leaving only the hydraulic flow in the braking channel 8 to hinder the rotation of the cup-shaped vane 2. This is used to balance or resist the positive torque added to the cup-shaped vane 2 by the oil inlet 4, hindering the rotation of the impeller, thereby enabling the output wheel shaft 3 to achieve flexible semi-braking.

[0055] This application utilizes the absorption and reuse of pulsating energy in the shock channel 6. There is no need to install a safety valve with overload protection function at the front end of the motor. Instead, the shock wave recoverer 12 at the bottom of the shock channel 6 recovers and converts the pulsating shock wave energy, thereby eliminating the waste of pulsating impact energy caused by the safety valve. This makes full use of energy transmission and overcomes unnecessary energy loss. Furthermore, by setting up the flow channel 9 to reuse the recovered and converted pulsating shock wave energy, it also ensures an increase in motor output torque and improved operational stability.

[0056] In a preferred embodiment, the axis of the oil outlet 5 is tangent to the center line of the rotation trajectory of the cup-shaped blade 2, and the bottom of the cup-shaped blade 2 at the tangent point is directly opposite the oil outlet 5.

[0057] Furthermore, the centerlines of oil outlet 5 and oil inlet 4 may be collinear or non-collinear.

[0058] Furthermore, at least three cup-shaped blades can be retained in the cavity between the oil outlet 5 and the oil inlet 4 to ensure smooth torque and full energy utilization.

[0059] When the center lines of oil outlet channel 5 and oil inlet channel 4 are collinear, oil outlet channel 5 and the accommodating cavity can adopt a snail shell structure.

[0060] When the centerlines of the oil outlet 5 and the oil inlet 4 are not on the same straight line, the purpose is to increase the flow path of the oil, increase the power utilization rate, and reduce turbulence, pressure fluctuations, or air bubbles.

[0061] In a preferred embodiment, the angle between the flow channel 9 and the oil inlet channel 4 is less than 90°; or, the angle between the braking channel 8 and the oil outlet channel 5 is greater than 90°.

[0062] When the flow-aiding control valve 10 is opened, the pressure fluid in the flow-aiding channel 9 assists the oil inlet channel 4 to increase the rotational energy input to the cup-shaped blade 2; when the brake control valve 11 is opened and the flow-aiding control valve 10 is closed, the pressure fluid in the brake channel 8 obstructs the outflow of the oil outlet channel 5 or obstructs the rotation of the cup-shaped blade 2.

[0063] When the flow-aiding control valve 10 and the braking control valve 11 are opened simultaneously, the cup-shaped vane 2 is driven by the shock wave pulsating flow and differential pressure flow from the oil inlet 4 to rotate the output wheel shaft 3. After the shock wave pulsating flow is absorbed by the shock wave recoverer 12 in the shock wave channel 6, the hydraulic flow with stable pressure is released into the flow-aiding channel 9 and the braking channel 8. The hydraulic flow entering the braking channel 8 hinders the rotation of the cup-shaped vane 2, thereby offsetting the positive torque added to the output wheel shaft 3 by the hydraulic flow in the flow-aiding channel 9. At this time, the flow-aiding control valve 10 is closed while the braking control valve 11 is kept open. The positive torque added to the output wheel shaft 3 by the hydraulic flow in the flow-aiding channel 9 disappears, leaving only the hydraulic flow in the braking channel 8 to hinder the rotation of the cup-shaped vane 2. This is used to balance or resist the positive torque added to the cup-shaped vane 2 by the oil inlet 4, hindering the rotation of the impeller, thereby enabling the output wheel shaft 3 to achieve flexible semi-braking.

[0064] In a preferred embodiment, the output shaft 3 includes an output shaft body 31 and an output shaft 32; the output shaft 32 body is connected inside the motor body 1; the output shaft body 31 includes a wheel 311 and a rotating shaft 312, the wheel 311 is circumferentially connected with a plurality of cup-shaped blades 2, the rotating shaft 312 is fixedly connected to the wheel 311, and both ends of the rotating shaft 312 are respectively connected to the bearing end cap in the bearing support hole inside the motor body 1 through dynamic seals; the output shaft 32 passes through the bearing end cap and the rotating shaft 312, and the output shaft 32 is fixedly connected to the rotating shaft 312 through a key or spline.

[0065] The wheel 311 can be configured with a spoke structure for use in large motor drives, thereby reducing the motor's own starting inertia and increasing the motor's external starting torque. A maintenance window is provided on the outer side of the motor cover and / or motor base, which contains a cavity for accommodating the cup-shaped blade 2. This allows for timely shutdown when the sensor detects damage to the cup-shaped blade 2, enabling inspection or replacement of the damaged blade or tightening of the cup-shaped blade 2 through the maintenance window.

[0066] The output shaft 32 is independent of the motor body 1. The output shaft 32 can be installed on the side of the motor cover or the side of the motor base for different output directions and rotation directions, which is convenient for on-site installation.

[0067] The rotary shaft 312 is inserted into or integrated with the wheel 311. When the rotary shaft 312 and the wheel 311 are integrated, it is installed in the motor body 1 through a separate design of the motor cover and the motor base. Furthermore, the rotary shaft 312 is mounted in bearing support holes on the motor cover and the motor base via bearings. Bearing end caps are connected to the bearing support holes, and both ends of the rotary shaft 312 are connected to the bearing end caps in the bearing support holes within the motor body 1 via dynamic seals. In addition, the bearing end caps and the rotary shaft 312 are hollow, and the hollow portion of the rotary shaft 312 is provided with splines or keyways for fixed connection with the output shaft 32.

[0068] By placing the bearing end cover on the rotating shaft 312, which is farther away from the cup-shaped blade 2, the linear velocity of the rotating shaft 312 is reduced, and the life of the dynamic seal is enhanced. The static seal is set between the motor base and the motor cover, which enhances reliability and thus improves the service life of the entire energy-saving fluid motor that can withstand high pressure and pressure pulsation.

[0069] In a preferred embodiment, the cup-shaped blade 2 includes a cup-shaped blade body 21 and a connector 22; the cup-shaped blade body 21 adopts a gourd-shaped, hemispherical, or multi-arc structure; the connector 22 protrudes and is connected to one side of the cup-shaped blade body 21; a plurality of insertion slots for inserting the connector 22 are provided on the circumferential end face of the wheel 311, and the connector 22 is connected to both sides along the axial direction by insertion locking devices. The insertion locking devices limit the connector 22 in the axial direction, so that after the connector 22 is locked and connected to the turntable, the cup-shaped blade 2 is connected to the circumference of the turntable.

[0070] The connector 22 has a columnar structure and protrudes along the axial direction to connect to both sides of the cup-shaped blade body 21, so that the connector 22 can be inserted into the insertion slot and both ends of the connector 22 can extend out of the insertion slot, which facilitates the installation of the two ends of the connector 22 with the insertion locking device. The length of the connector 22 is greater than the thickness of the cup-shaped blade body 21 along the axial direction, so as to reserve an installation position for the insertion locking device.

[0071] The locking device can be made of spring pins or snap fasteners. When spring pins are used, through holes are made at both ends of the connector 22 in the radial direction. The spring pins are then inserted into the through holes. After the spring snap fasteners of the spring pins are engaged, they will restrict the movement of the connector 22 in the axial direction in the insertion groove. Thus, the spring pins at both ends of the connector 22 are used to limit the axial movement of the connector 22, thereby further strengthening the tightness of the connection between the connector 22 and the wheel 311. The cup-shaped blade 2 will not detach from the wheel 311 as the wheel 311 rotates, thus improving the connection strength.

[0072] In a preferred embodiment, the connector 22 has a main body with an annular structure and a connecting segment that is arc-shaped to the main body; one end of the connecting segment is tangentially connected to the outer periphery of the main body, and the other end of the connecting segment is tangentially connected to the cup-shaped blade 2.

[0073] By setting the connecting end with an arc shape and the main body of the connector 22 with an annular structure, the connector 22 can be connected to the circular insertion slot, and the cup-shaped blade 2 on the other side of the connector 22 can form a certain angle with the radial direction of the wheel 311, so that the cup-shaped blade 2 surrounds the wheel 311 in an annular shape.

[0074] In a preferred embodiment, the braking channel 8 includes a first fluid section 81 and a second fluid section 82; the first fluid section 81 is connected to the second fluid section 82, the first fluid section 81 is connected to the recovery channel, and the second fluid section 82 is connected to the accommodating cavity or to the oil outlet channel 5.

[0075] Furthermore, the first fluid segment 81 is vertically connected to the shock channel 6; or, the first fluid segment 81 is obliquely connected to the shock channel 6.

[0076] In a preferred embodiment, the flow channel 9 includes a third fluid section 91 and a fourth fluid section 92; the third fluid section 91 is connected to the fourth fluid section 92, the third fluid section 91 is connected to the shock channel 6, and the fourth fluid section 92 is connected to the accommodating cavity or to the oil inlet channel 4.

[0077] In a preferred embodiment, the motor of this application that withstands large pulsating flow further includes a sensor, which is disposed outside the motor cover and / or motor base outside the rotating cavity accommodating the cup-shaped blade 2 of the motor body 1; the sensor measures the outlet flow volume V of the oil passage. 1i The time T required for outflow 1i The number n of cup-shaped blades passing through 1i The average time t between two adjacent cup-shaped blades 1i Through the formula:

[0078] q 1i =Q 1i / (n 1i ×t 1i )=(V 1i / T 1i ) / (n 1i ×t 1i )

[0079] In the formula, Q 1i This represents the flow rate through the cup-shaped blades each time.

[0080] The displacement q of each passage through the cup-shaped blades can be obtained.1i The average displacement q of the motor is obtained by averaging the displacement measurements from each measurement.

[0081] q=(q 11 +q 12+...+ q 1i ) / i

[0082] In the formula, q is the average displacement of the motor, q 11 For the first displacement through the cup-shaped blades, q 12 For the second passage through the cup-shaped blades, q 1i Let i be the displacement of the i-th time through the cup-shaped blade, where i ≥ 3.

[0083] It should be noted that the number of cup-shaped blades evenly distributed around the circumference of the wheel can be selected in various ways, with the preferred number being n, which fills the insertion slots. 1i For standard specifications, besides filling all the slots, the cup-shaped blades may not need to fill all the slots. In this case, the number of cup-shaped blades that can be evenly distributed is n. ji However, j must not be less than 3. At least 3 cup-shaped blades 2 can be retained in the cavity between the oil outlet 5 and the oil inlet 4 to ensure smooth torque and full energy utilization.

[0084] For any parts not mentioned in this application, existing technologies may be used or referenced.

[0085] The various embodiments in this specification are described in a progressive manner. The same or similar parts between the various embodiments can be referred to each other. Each embodiment focuses on describing the differences from other embodiments.

[0086] The above description is merely an embodiment of this application and is not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principle of this application should be included within the scope of the claims of this application.

Claims

1. An energy saving fluid motor resistant to high pressure and pressure pulsation, characterized by, The motor body, cup-shaped blades, output wheel shaft and shock wave collector are included; the output wheel shaft is connected with a plurality of cup-shaped blades on the outer periphery; the motor body includes symmetrically connected motor cover and motor base, and the motor cover and the motor base are formed with accommodating cavities accommodating the cup-shaped blades and the output wheel shaft, and the output wheel shaft is supported outwardly to transmit power through the bearings on the motor cover and the motor base; the motor body is also provided with oil inlet channel and oil outlet channel, the axis of the oil inlet channel is tangent to the center line of the rotating track of the cup-shaped blades, the cup opening of the cup-shaped blades at the tangent position is opposite to the oil inlet channel, and the shock wave channel is arranged vertically to the axis of the oil inlet channel or within the range of 120° angle; the one-way valve is arranged on the shock wave channel to ensure that the shock wave reaches the shock wave collector at the bottom of the shock wave channel in a single direction; The flow assisting channel and the braking channel are respectively communicated on both sides of the bottom of the shock wave channel; the outlet of the flow assisting channel is opposite or perpendicular to the cup opening of the cup-shaped blade, and the outlet of the braking channel is opposite or perpendicular to the cup bottom of the cup-shaped blade, so as to ensure that the liquid flow in the flow assisting channel and the braking channel is consistent with the rotating direction of the cup-shaped blade or hits the top; the flow assisting control valve is connected in the flow assisting channel, and the braking control valve is connected in the braking channel; The large pulsating flow passes through the shock wave collector at the bottom of the shock wave channel, is boosted and stabilized after the shock wave, and then enters the flow assisting channel and the braking channel on both sides; when the flow assisting control valve is opened, the cup-shaped blade is rotated under the impact of the incoming flow in the oil inlet channel and the flow assisting channel; when the braking control valve is opened, the pulsating flow sent to the cup-shaped blade by the braking channel after being boosted and stabilized hinders the rotation of the cup-shaped blade, so that the output wheel shaft can realize flexible semi-braking under the action of opposite torques.

2. The energy saving fluid motor resistant to high pressure and pressure pulsation as claimed in claim 1 wherein, The axis of the oil outlet channel is tangent to the center line of the rotating track of the cup-shaped blades, and the cup bottom of the cup-shaped blade at the tangent position is opposite to the oil outlet channel; the axis of the oil outlet channel and the oil inlet channel is collinear or not collinear; At least three cup-shaped blades can be stored in the accommodating cavity between the oil outlet channel and the oil inlet channel, so as to ensure that the torque is stable and the energy is fully utilized; When the center lines of the oil outlet channel and the oil inlet channel are collinear, the oil outlet channel and the accommodating cavity can adopt a snail shell structure.

3. An energy efficient fluid motor resistant to high pressure and pressure pulsations as claimed in claim 2 wherein, The angle between the flow assisting channel and the oil inlet channel is less than 90°; or, the angle between the braking channel and the oil outlet channel is greater than 90°; When the flow assisting control valve is opened, the pressure fluid in the flow assisting channel assists the oil inlet channel to increase the rotating energy input of the cup-shaped blade; when the braking control valve is opened and the flow assisting control valve is closed, the pressure fluid in the braking channel hinders the outflow of the oil outlet channel or hinders the rotation of the cup-shaped blade.

4. The energy efficient fluid motor that is resistant to high pressure and pressure pulsation as claimed in claim 1 wherein, The output wheel shaft includes output wheel shaft body and output shaft; the output wheel shaft body is connected in the motor body; the output wheel shaft body includes wheel disc and rotary shaft, the wheel disc is circumferentially connected with a plurality of cup-shaped blades, the rotary shaft is fixedly connected with the wheel disc, and the both ends of the rotary shaft are respectively connected with the bearing end covers in the bearing support holes in the motor body through dynamic seals; the output shaft passes through the bearing end covers and the rotary shaft, and the output shaft is fixedly connected with the rotary shaft through keys or splines.

5. An energy efficient fluid motor resistant to high pressure and pressure pulsations as claimed in claim 4 wherein, The cup-shaped blade comprises a cup-shaped blade body and a connecting piece; the cup-shaped blade body adopts a water ladle shape, a hemispherical shape or a multi-arc surface structure; the connecting piece is protrusively connected to one side of the cup-shaped blade body; a plurality of plug-in grooves for plugging the connecting piece are arranged on the circumferential end surface of the wheel disc in the circumferential direction; the connecting piece is connected with plug-in locking devices on both sides in the axial direction, and the plug-in locking devices are used to limit the connecting piece in the axial direction, so that the connecting piece is locked with the wheel disc after being connected with the wheel disc, and the cup-shaped blade is connected to the wheel disc.

6. An energy efficient fluid motor resistant to high pressure and pressure pulsations as claimed in claim 5 wherein, The connecting piece has a connecting piece body with a ring shape and a connecting section which is connected with the connecting piece body in an arc shape; one end of the connecting section is tangentially connected with the outer periphery of the connecting piece body, and the other end of the connecting section is tangentially connected with the cup-shaped blade.

7. The energy efficient fluid motor that is resistant to high pressure and pressure pulsation as claimed in claim 1 wherein, The brake channel comprises a first fluid section and a second fluid section; the first fluid section is in communication with the second fluid section, the first fluid section is in communication with the recovery channel, and the second fluid section is in communication with the accommodating cavity or the oil outlet.

8. An energy efficient fluid motor resistant to high pressure and pressure pulsations as claimed in claim 7 wherein, The first fluid section is vertically connected with the shock wave channel; or the first fluid section is obliquely connected with the shock wave channel.

9. The energy efficient fluid motor that is resistant to high pressure and pressure pulsation as claimed in claim 1 wherein, The flow assisting channel comprises a third fluid section and a fourth fluid section; the third fluid section is in communication with the fourth fluid section, the third fluid section is in communication with the shock wave channel, and the fourth fluid section is in communication with the accommodating cavity or the oil inlet.

10. The energy efficient fluid motor that is resistant to high pressure and pressure pulsation as claimed in claim 1 wherein, The sensor is arranged outside the motor cover and / or the motor base outside the cup-shaped blade rotary cavity of the motor body. The volume of the flow V at the outlet of the oil duct is measured by a sensor 1i and the length of time T required for the outflow 1i , the number of cups n passed by 1i , the average length of time t passed between two adjacent cups 1i by the formula: q 1i = Q 1i / (n 1i × t 1i ) = (V 1i / T 1i ) / (n 1i × t 1i ) wherein Q 1i is the flow rate per pass of the cup blade; The volume q delivered per pass by the cup-shaped blade 1i The average volume delivered q by the motor is obtained by averaging the volume delivered per pass q = (q 11 + q 12 +... + q 1i ) / i where q is the average displacement of the motor, q 11 is the first pass through the cup blade displacement, q 12 is the second pass through the cup blade displacement, q 1i is the i-th pass through the cup blade displacement, with i≥3.

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