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

Abstract

The invention 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 technical field of hydraulic motors, and particularly relates to an energy-saving fluid motor that can withstand high pressure and pressure pulsation. Background Art

[0002] A hydraulic motor is also called a hydraulic starter or a hydraulic starting machine. Its working principle is to use liquid as the working medium and utilize the kinetic energy of the liquid rather than the pressure difference energy of the hydraulic pressure to transfer energy, which is a fluid drive. Hydraulic motors generally need to rotate forward and backward, so they should have symmetry in the internal structure. However, the drive of a large mixer is generally unidirectional rotation, and the large mixer requires a rotational speed lower than 500 r / min, and a low-speed hydraulic motor is needed without the requirement of forward and backward rotation.

[0003] The main characteristics of existing low-speed hydraulic motors are large displacement, large volume, and low rotational speed. Therefore, they can be directly connected to the transmission mechanism without a reduction device, simplifying the transmission mechanism. For a general vane hydraulic motor, a spring must be installed at the root of the vane of the hydraulic motor to ensure that the vane always adheres to the inner surface of the stator. Relying on the high-speed rotation of the vane and the rotor together, the vane always adheres to the inner surface of the stator to play the role of sealing oil and form a working volume so that the motor can start normally.

[0004] A hydraulic motor must have a large starting torque. The so-called starting torque is the torque that can be output on the motor shaft when the motor starts from a stationary state. This torque is usually greater than the torque in the running state at the same working pressure difference. Therefore, in order to make the starting torque as close as possible to the torque in the working state, it is required that the torque pulsation of the motor is small and the internal friction is small. Moreover, in order to have an overload protection function, a safety valve needs to be installed near the hydraulic motor.

[0005] There is currently no low-speed stable torque hydraulic fluid motor on the market that can combine the momentum of the fluid (flow velocity V) and the pressure difference energy of the fluid (ΔP) for application. Therefore, it cannot be directly applied to a discrete flow transmission and control system of a hydraulic quasi-rigid pipeline. Because, for the quasi-rigidity in a discrete flow transmission and control system of a hydraulic quasi-rigid pipeline, a relatively high hydraulic energy is required in the fluid pipeline, such as greater than 10 MPa and above. In order to achieve high-speed transmission, there is also a high-speed pulsating shock wave flow. If this energy is converted into the fluid kinetic energy of large flow and high speed and then the work is carried out through a conventional hydraulic motor, these conversion losses may exceed the original intention of reducing the energy consumption and improving the transmission speed for long-distance high-speed hydraulic pipeline transmission; if the energy transmitted through such pipelines is directly connected to a hydraulic motor, it will cause the instability of the motor operation due to the large and numerous pulsations in the incoming pipeline, and it is difficult to control the output speed and torque. Moreover, for the safety function of the overload protection function, the safety valve installed at the front end of the motor will often be impacted and opened by the pulsating shock wave, resulting in energy leakage during transmission.

[0006] Therefore, there is an urgent need for an energy-saving fluid motor that can withstand high pressure and pressure pulsation. Summary of the Invention

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

[0008] The technical solution adopted by the present application is as follows:

[0009] An energy-saving fluid motor that can withstand high pressure and pressure pulsation includes a motor body, cup-shaped blades, an output wheel shaft, and a shock wave recovery device; a plurality of cup-shaped blades are connected to the outer periphery of the output wheel shaft; the motor body includes a symmetrically connected motor cover and a motor base, and a receiving cavity for accommodating the cup-shaped blades and the output wheel shaft is formed inside the motor cover and the motor base. The output wheel shaft is supported by bearings on the motor cover and the motor base to transmit power outward; the motor body is also provided with an oil inlet channel and an oil outlet channel. The axis of the oil inlet channel is tangent to the center line of the rotation trajectory of the cup-shaped blades. At the tangent point, the cup mouth of the cup-shaped blade faces the oil inlet channel, and a shock wave channel is arranged perpendicular to the axis of the oil inlet channel or within an included angle range of 120°; a one-way valve is arranged on the shock wave channel to ensure that the shock wave reaches the shock wave recovery device at the bottom of the shock wave channel in a single direction.

[0010] On both sides of the bottom of the shock wave channel, a flow assistance channel and a braking channel are respectively communicated; the outlet of the flow assistance 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 to ensure that the liquid flow inside is consistent with or impacts the rotation direction of the cup-shaped blade; a flow assistance control valve is connected inside the flow assistance channel, and a braking control valve is connected inside the braking channel.

[0011] After the large pulsation flows through the shock wave recovery device at the bottom of the shock wave channel, the shock wave is boosted in pressure and stabilized, and then enters the flow assistance channels and the braking channels on both sides; when the flow assistance control valve is opened, the cup-shaped blades drive the output wheel shaft to rotate under the impact of the incoming flow in the oil inlet channel and the flow assistance channel; when the braking control valve is opened, the braking channel sends the pulsating flow after being boosted in pressure and stabilized into the cup-shaped blades, hindering the rotation of the cup-shaped blades, so that the output wheel shaft can achieve flexible semi-braking under the action of the opposite torque.

[0012] Under normal working conditions, the flow-assisting control valve is normally open and the braking control valve is closed. The cup-shaped vane drives the output wheel shaft to rotate under the impact of the incoming flow in the oil inlet passage. The incoming flow in the oil inlet passage contains a shock wave pulsation part, which is boosted after the pulsating energy is absorbed by the shock wave recovery device in the shock wave passage. The hydraulic fluid with stable pressure flows to the flow-assisting passage and then reaches the cup-shaped vane opposite to the oil inlet passage. The shock wave recovery energy is used to assist the impeller to rotate, giving an additional positive torque to the output wheel shaft. In the braking working state, the flow-assisting control valve is normally open and the braking control valve is open. The braking passage sends the hydraulic fluid recovered by the shock wave to the cup-shaped vane opposite to the oil outlet passage, hindering the rotation of the cup-shaped vane, so that the output wheel shaft can be flexibly braked under the action of the opposite torque.

[0013] The axis of the oil outlet passage is tangent to the center line of the rotation trajectory of the cup-shaped vane, and the bottom of the cup of the cup-shaped vane is facing the oil outlet passage at the tangent point; the axis lines of the oil outlet passage and the oil inlet passage are collinear or non-collinear; at least 3 cup-shaped vanes can be retained in the accommodation 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 accommodation cavity can adopt a snail shell structure.

[0014] The included angle between the flow-assisting passage and the oil inlet passage is less than 90°; or, the included angle between the braking passage and the oil outlet passage is greater than 90°; when the flow-assisting control valve is opened, the pressure fluid in the flow-assisting passage assists the oil inlet passage to increase the rotational energy input to the cup-shaped vane; when the braking control valve is opened and the flow-assisting control valve is closed, the pressure fluid in the braking passage hinders the outflow of the oil outlet passage or hinders the rotation of the cup-shaped vane.

[0015] The output wheel shaft includes an output wheel shaft body and an output shaft; the output shaft body is connected to the inside of the motor body; the output wheel shaft body includes a wheel disc and a rotating shaft. A plurality of cup-shaped vanes are circumferentially connected to the wheel disc. The rotating shaft is fixedly connected to the wheel disc. 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 cap and the rotating shaft, and the output shaft is fixedly connected to the rotating shaft through a key or spline.

[0016] The cup-shaped vane includes a cup-shaped vane body and a connecting piece; the cup-shaped vane body adopts a ladle-shaped, hemispherical structure or a multi-arc surface structure; the connecting piece protrudes and is connected to one side of the cup-shaped vane body; a plurality of insertion slots for inserting the connecting piece are circumferentially opened on the circumferential end surface of the wheel disc. The connecting piece is connected with insertion locking devices on both sides along the axial direction, and the connecting piece is axially limited through the insertion locking devices, so that after the connecting piece is locked and connected to the turntable, the cup-shaped vane is connected to the turntable circumference.

[0017] The connecting piece has a connecting piece body with an annular structure and a connecting section that is arc-connected to the connecting piece body; one end of the connecting section is tangentially connected to the outer circumference of the connecting piece body, and the other end of the connecting section is tangentially connected to the cup-shaped vane.

[0018] The braking channel includes 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 accommodation cavity or the oil outlet channel.

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

[0020] The flow assistance channel includes 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 channel, and the fourth fluid section is in communication with the accommodation cavity or the oil inlet channel.

[0021] An energy-saving fluid motor resistant to high pressure and pressure pulsation further includes a sensor, and the sensor is arranged outside the motor cover and / or the motor seat outside the accommodation cup-shaped vane rotary cavity of the motor body;

[0022] Measure the outlet flow volume V of the oil outlet channel through the sensor 1i and the time length T required for the outflow 1i , the number n of cup-shaped vanes passed through 1i , the average time t between two adjacent cup-shaped vanes passing through 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 is the flow rate passing through the cup-shaped vane each time;

[0025] The displacement q passing through the cup-shaped vane each time can be obtained 1i , and the average value of the displacement measured each time is taken to obtain the average displacement q of the motor as:

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

[0027] In the formula, q is the average displacement of the motor, q 11 is the displacement passing through the cup-shaped vane for the first time, q 12 is the displacement passing through the cup-shaped vane for the second time, q 1i is the displacement passing through the cup-shaped vane for the i-th time, and the number of times i≥3.

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

[0029] 1. An energy-saving fluid motor resistant to high pressure and pressure pulsation, comprising a motor body, cup-shaped blades, an output wheel shaft and a shock wave recovery device; a plurality of cup-shaped blades are connected to the outer periphery of the output wheel shaft; the motor body includes a symmetrically connected motor cover and a motor base, and an accommodation cavity for accommodating the cup-shaped blades and the output wheel shaft is formed inside the motor cover and the motor base. The output wheel shaft is supported by bearings on the motor cover and the motor base to transmit power outward; the motor body is also provided with an oil inlet channel and an oil outlet channel. The axis of the oil inlet channel is tangent to the center line of the rotation trajectory of the cup-shaped blades. At the tangent point, the cup mouth of the cup-shaped blade faces the oil inlet channel, and a shock wave channel is arranged within a range perpendicular to the axis of the oil inlet channel or at an angle of 120°. A one-way valve is arranged on the shock wave channel to ensure that the shock wave reaches the shock wave recovery device at the bottom of the shock wave channel in a single direction.

[0030] Under normal working conditions, the flow assistance 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 of the oil inlet channel. The incoming flow of the oil inlet channel includes a shock wave pulsation part, which is boosted after the pulsating energy is absorbed by the shock wave recovery device of the shock wave channel. The hydraulic fluid after being stabilized in pressure flows to the flow assistance channel and then reaches the cup-shaped blade opposite to the oil inlet channel. The shock wave recovery energy is used to assist the impeller to rotate, giving an additional positive torque to the output wheel shaft; under the braking working condition, the flow assistance control valve is normally open and the braking control valve is opened. The braking channel sends the hydraulic fluid recovered by the shock wave to the cup-shaped blade opposite to the oil outlet channel, hindering the rotation of the cup-shaped blade, so that the output wheel shaft can be flexibly braked under the action of the opposite torque.

[0031] This application utilizes the reuse of the pulsating energy absorbed by the shock wave channel. There is no need to set a safety valve with an overload protection function at the front end of the motor. Instead, the shock wave recovery device at the bottom of the shock wave channel recovers and converts the pulsating shock wave energy, thus eliminating the waste of pulsating shock energy caused by the safety valve, and then making full use of the transmitted energy, overcoming unnecessary energy losses, and by setting a flow assistance channel to reuse the recovered and converted pulsating shock wave energy, further ensuring the increase of the output torque of the motor and the improvement of the operation stability.

[0032] 2. As a preferred embodiment of the present application, the output wheel shaft includes an output wheel shaft body and an output shaft; the output shaft body is connected inside the motor body; the output wheel shaft body includes a wheel disc and a rotating shaft. A plurality of cup-shaped blades are circumferentially connected to the wheel disc. The rotating shaft is connected to the wheel disc, and both ends of the rotating shaft are respectively connected to the bearing end covers in the bearing support holes inside the motor body through dynamic seals; the output shaft passes through the bearing end cover and the rotating shaft, and the output shaft is fixedly connected to the rotating shaft by a key or a spline.

[0033] Both ends of the rotating shaft are respectively connected to the bearing end caps in the bearing support holes inside the motor body through dynamic seals; the output shaft has nothing to do with the dynamic seals, thus reducing the seal leakage in the movement of the output shaft. The output shaft has nothing to do with the motor body. The bearing end cap and the rotating shaft are hollow, and splines or key grooves are arranged in the hollow part of the rotating shaft for fixed connection with the output shaft. Thus, the installation position of the output shaft can be conveniently changed, which brings convenience to the motor rotation direction and installation on site.

[0034] 3. As a preferred embodiment of the present application, the flow assistance channel can be connected to the oil inlet channel at an angle less than 90°, or the braking channel can be connected to the oil outlet channel at an angle greater than 90°. When the flow assistance control valve is opened, the pressure fluid in the flow assistance channel assists the oil inlet channel to increase the rotational energy input to the cup-shaped blade; when the braking control valve is opened and the flow assistance 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.

[0035] When the flow assistance control valve and the braking control valve are opened simultaneously, the cup-shaped blade drives the output wheel shaft to rotate under the push of the shock pulsating flow and the pressure difference flow of the incoming flow in the oil inlet channel; after the shock pulsating flow undergoes energy pulsation absorption by the shock recovery device in the shock channel, the hydraulic flow with stable pressure is released into the flow assistance channel and the braking channel. The hydraulic flow entering the braking channel hinders the rotation of the cup-shaped blade, thereby offsetting the additional positive torque given to the output wheel shaft by the hydraulic flow in the flow assistance channel; at this time, then close the flow assistance control valve and keep the braking control valve open, the additional positive torque given to the output wheel shaft by the hydraulic flow in the flow assistance channel disappears, and only the hydraulic flow in the braking channel hinders the rotation of the cup-shaped blade, which is used to balance or resist the additional positive torque of the oil inlet channel on the cup-shaped blade and hinder the rotation of the impeller, so that the output wheel shaft can achieve flexible semi-braking.

[0036] 4. As a preferred embodiment of the present application, the wheel disc is provided with a plurality of plug-in slots and plug-in locking devices for plug-in connection of the cup-shaped blades along the circumferential direction. The number of cup-shaped blades evenly distributed on the circumference of the wheel disc can be selected in various ways. Preferably, the number n of cup-shaped blades filling the plug-in slots 1i is the standard specification, and the number of other evenly distributed cup-shaped blades is n ji , but j cannot be less than 3, which is convenient for evenly increasing n 1i , for changing the displacement q 1i , and enhancing the torque N = ΔP × q 1i , where ΔP is the pressure difference of the liquid.

[0037] 5. At least 3 cup-shaped blades can be retained in the accommodation cavity between the oil outlet channel and the oil inlet channel to ensure smooth torque and full utilization of energy; and when the center lines of the oil outlet channel and the oil inlet channel are collinear, the oil outlet channel and the accommodation cavity can adopt a snail shell structure; the full energy of the impact fluid can be utilized more effectively.

[0038] 6. The roulette can be set as a spoke structure for large motor drive to reduce the starting inertia of the motor itself and increase the starting torque of the motor to the outside. A maintenance window is opened on the outside of the motor cover and / or the motor base that forms a cavity for accommodating cup-shaped vanes in the motor body, so that when the sensor detects damaged cup-shaped vanes, the machine can be stopped in time to view or replace the damaged cup-shaped vanes or fasten the cup-shaped vanes through the maintenance window. In addition, the bearing cover is far from the cavity for accommodating cup-shaped vanes at the rotating shaft, so the linear velocity of the dynamic seal contact lip of the bearing cover at the rotating shaft is small, and the service life of the dynamic seal is long. The connection between the motor cover and / or the motor base of the split motor adopts static seal, which is also reliable. Therefore, the seal life can be effectively improved and the service life of the motor can be extended. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] The drawings described herein are used to provide a further understanding of the present application and form a part of the present application. The schematic embodiments of the present application and their descriptions are used to explain the present application and do not constitute an improper limitation of the present application. In the drawings:

[0040] Figure 1 is a schematic structural diagram of an energy-saving fluid motor resistant to high pressure and pressure pulsation under an embodiment of the present application;

[0041] Figure 2 is a schematic structural diagram of the output wheel shaft of an energy-saving fluid motor resistant to high pressure and pressure pulsation under an embodiment of the present application;

[0042] In the drawings,

[0043] 1, motor body; 2, cup-shaped vane; 21, cup-shaped vane body; 22, connecting piece; 3, output wheel shaft; 31, output wheel shaft body; 311, roulette; 312, rotating shaft; 32, output shaft; 4, oil inlet channel; 5, oil outlet channel; 6, shock wave channel; 7, one-way valve; 8, braking channel; 81, first fluid section; 82, second fluid section; 9, flow assisting channel; 91, third fluid section; 92, fourth fluid section; 10, flow assisting control valve; 11, braking control valve; 12, shock wave recovery device. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0044] In order to more clearly illustrate the overall concept of the present application, the following will be described in detail by way of examples with reference to the accompanying drawings of the specification.

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

[0046] In addition, in the description of the present application, it should be understood that the orientation or positional relationship indicated by terms such as "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the present invention.

[0047] In the present application, unless otherwise clearly specified and defined, terms such as "installed", "connected", "connected to", "fixed", etc. should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or integrated; it can be a mechanical connection, an electrical connection, or a communication connection; it can be directly connected, or indirectly connected through an intermediate medium, and can be the communication inside two elements or the interaction relationship between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0048] In the present application, unless otherwise clearly specified and defined, the first feature being "on" or "under" the second feature can be that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. In the description of this specification, the description referring to terms such as "embodiment", "example", "an embodiment", "example", or "specific example", etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0049] The present application relates to an energy-saving fluid motor that can withstand high pressure and pressure pulsation, as Figure 1-2 shown, which includes a motor body 1, cup-shaped blades 2, an output wheel shaft 3, and a shock wave recovery device 12; a plurality of cup-shaped blades 2 are connected to the outer periphery of the output wheel shaft 3; the motor body 1 includes a symmetrically connected motor cover and a motor seat, and an accommodation cavity for accommodating the cup-shaped blades 2 and the output wheel shaft 3 is formed inside the motor cover and the motor seat. The output wheel shaft 3 is supported by bearings on the motor cover and the motor seat to transmit power outward; the motor body 1 is also provided with an oil inlet passage 4 and an oil outlet passage 5. The axis of the oil inlet passage 4 is tangent to the center line of the rotation trajectory of the cup-shaped blade 2. At the tangent point, the cup mouth of the cup-shaped blade 2 faces the oil inlet passage 4, and a shock wave channel 6 is arranged within a range perpendicular to the axis of the oil inlet passage 4 or at an angle of 120°; a one-way valve 7 is arranged 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 two sides of the bottom of the shock channel 6 are connected with a flow-assisting channel 9 and a brake channel 8 respectively; the outlet of the flow-assisting channel 9 is opposite to or perpendicular to the cup mouth of the cup-shaped blade 2, and the outlet of the brake 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 therein is consistent with the rotation direction of the cup-shaped blade 2 or hits the top; the flow-assisting channel 9 is connected with a flow-assisting control valve 10, and the brake channel 8 is connected with a brake control valve 11;

[0051] The large pulsating flow passes through the shock wave recoverer 12 at the bottom of the shock wave channel, and then the pressure is increased and stabilized after the shock wave, and then enters the flow-aiding channel 9 and the brake channel 8 on both sides; when the flow-aiding 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 channel and the flow-aiding channel; when the brake control valve 11 is opened, the brake channel 8 sends the pulsating flow after pressure increase and stabilization to the cup-shaped blades 2, hindering 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 working conditions, the flow-assisting control valve 10 is normally open and the brake 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 from the oil inlet channel 4. The incoming flow from the oil inlet channel 4 includes the shock wave pulsation part, which is boosted after absorbing the pulsation energy through the shock wave recovery device 12 of the shock wave channel 6. The hydraulic pressure with stabilized pressure flows to the flow-assisting channel 9, and then reaches the cup-shaped blade 2 opposite to the oil inlet channel 4, and uses the shock wave recovery energy to assist the impeller to rotate, giving the output wheel shaft 3 additional positive torque; under braking working conditions, the flow-assisting control valve 10 is normally open and the brake control valve 11 is opened. The brake channel 8 sends the hydraulic flow recovered by the shock wave to the cup-shaped blade 2 opposite to the oil outlet channel 5, hindering the rotation of the cup-shaped blade 2, so that the output wheel shaft 3 can be flexibly braked under the action of the opposite torque.

[0053] Specifically, under normal working conditions, the flow-assisting control valve 10 is normally open and the brake control valve 11 is closed, and the cup-shaped blade 2 drives the output wheel shaft 3 to rotate under the impact of the incoming flow from the oil inlet channel 4; the incoming flow from the oil inlet channel 4 contains the shock wave pulsation part, which is boosted after absorbing the pulsation energy through the shock wave recovery device 12 of the shock wave channel 6, and the hydraulic pressure with stabilized pressure flows to the flow-assisting channel 9, and then reaches the cup-shaped blade 2 opposite to the oil inlet channel 4, and uses the shock wave recovery energy to assist the impeller to rotate, giving the output wheel shaft 3 additional positive torque; under braking working conditions, the flow-assisting control valve 10 is normally open and the brake control valve 11 is opened, and the cup-shaped blade 2 drives the output wheel shaft 3 to rotate. The blade 2 drives the output wheel shaft 3 to rotate under the impact of the incoming flow from the oil inlet channel 4; the incoming flow from the oil inlet channel 4 includes the shock wave pulsation part, which is boosted after absorbing the pulsation energy through the shock wave recovery device 12 of the shock wave channel 6, and the hydraulic flow with stabilized pressure flows to the flow-assisting channel 9, and then reaches the cup-shaped blade 2 opposite to the oil inlet channel 4, and uses the shock wave recovery energy to assist the impeller to rotate, giving the output wheel shaft 3 additional positive torque, and 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, hindering the rotation of the cup-shaped blade 2, so that the output wheel shaft 3 can be flexibly braked under the action of the opposite torque.

[0054] When the flow-assisting control valve 10 and the braking control valve 11 are opened simultaneously, the cup-shaped vane 2 drives the output wheel shaft 3 to rotate under the impetus of the shock pulse flow and the pressure difference flow of the incoming flow in the oil inlet passage 4; after the shock pulse flow undergoes energy pulsation absorption by the shock energy recovery device 12 in the shock passage 6, a hydraulic flow with stable pressure is released into the flow-assisting passage 9 and the braking passage 8. The hydraulic flow entering the braking passage 8 hinders the rotation of the cup-shaped vane 2, thereby offsetting the additional positive torque applied to the output wheel shaft 3 by the hydraulic flow in the flow-assisting passage 9. At this time, then close the flow-assisting control valve 10 while keeping the braking control valve 11 open. The additional positive torque applied to the output wheel shaft 3 by the hydraulic flow in the flow-assisting passage 9 disappears, and only the hydraulic flow in the braking passage 8 hinders the rotation of the cup-shaped vane 2, which is used to balance or resist the additional positive torque applied to the cup-shaped vane 2 by the oil inlet passage 4 and hinder the rotation of the impeller, so that the output wheel shaft 3 can achieve flexible semi-braking.

[0055] This application utilizes the reuse of the pulsating energy absorbed by the shock passage 6. There is no need to set a safety valve with an overload protection function at the front end of the motor. Instead, the shock energy recovery device 12 at the bottom of the shock passage 6 recovers and converts the pulsating shock energy, thereby eliminating the waste of pulsating shock energy caused by the safety valve, and further making full use of the transmitted energy, overcoming unnecessary energy losses, and through the setting of the flow-assisting passage 9, the pulsating shock energy recovered and converted is reused, and further ensuring the increase of the output torque of the motor and the improvement of the operating stability.

[0056] As a preferred embodiment, the axis of the oil outlet passage 5 is tangent to the center line of the rotation trajectory of the cup-shaped vane 2, and the bottom of the cup of the cup-shaped vane 2 at the tangent point faces the oil outlet passage 5.

[0057] Furthermore, the axis lines of the oil outlet passage 5 and the oil inlet passage 4 are collinear or non-collinear.

[0058] Even further, at least 3 cup-shaped vanes can be retained in the accommodation cavity between the oil outlet passage 5 and the oil inlet passage 4 to ensure smooth torque and full utilization of energy;

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

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

[0061] As a preferred embodiment, the included angle between the flow-assisting passage 9 and the oil inlet passage 4 is less than 90°; or, the included angle between the braking passage 8 and the oil outlet passage 5 is greater than 90°;

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

[0063] When the flow-assisting control valve 10 and the braking control valve 11 are opened simultaneously, the cup-shaped vane 2 drives the output wheel shaft 3 to rotate under the push of the shock pulse flow and the pressure difference flow of the incoming flow from the oil inlet channel 4; after the shock pulse flow absorbs the energy pulsation through the shock absorber 12 of the shock channel 6, a hydraulic flow with stable pressure is released into the flow-assisting channel 9 and the braking channel 8, and the hydraulic flow entering the braking channel 8 obstructs the rotation of the cup-shaped vane 2, thereby canceling the additional positive torque applied to the output wheel shaft 3 by the hydraulic flow in the flow-assisting channel 9; at this time, then close the flow-assisting control valve 10 while keeping the braking control valve 11 open, the additional positive torque applied to the output wheel shaft 3 by the hydraulic flow in the flow-assisting channel 9 disappears, and only the hydraulic flow in the braking channel 8 obstructs the rotation of the cup-shaped vane 2, which is used to balance or resist the additional positive torque applied to the cup-shaped vane 2 by the oil inlet channel 4 and obstruct the rotation of the impeller, so that the output wheel shaft 3 can achieve flexible semi-braking.

[0064] As a preferred embodiment, the output wheel shaft 3 includes an output wheel shaft body 31 and an output shaft 32; the output shaft 32 body is connected to the inside of the motor body 1; the output wheel shaft body 31 includes a wheel disc 311 and a rotating shaft 312, a plurality of cup-shaped vanes 2 are circumferentially connected to the wheel disc 311, the rotating shaft 312 is fixedly connected to the wheel disc 311, and both ends of the rotating shaft 312 are respectively connected to the bearing end caps in the bearing support holes in 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 a spline.

[0065] The wheel disc 311 can be set as a spoke structure for large motor drive to reduce the starting inertia of the motor itself and increase the starting torque of the motor to the outside. A maintenance window is opened on the outside of the motor cover and / or the motor base that forms an accommodation cavity for the cup-shaped vane 2 in the motor body, so that when the sensor detects a damaged cup-shaped vane 2, the machine can be stopped in time to view or replace the damaged cup-shaped vane or fasten the cup-shaped vane 2 through the maintenance window.

[0066] The output shaft 32 has nothing to do with the motor body 1, and the output shaft 32 can be installed on the motor cover side or the motor base side for different output directions and rotation directions, which is convenient for on-site installation.

[0067] The rotating shaft 312 is installed inside the wheel disc 311 or integrated with the wheel disc 311. When the rotating shaft 312 and the wheel disc 311 are of an integrated structure, it is installed in the motor body 1 through the design of separating the motor cover from the motor base. Moreover, the rotating shaft 312 is installed in the bearing support holes on the motor cover and the motor base through bearings, and a bearing end cover is connected inside the bearing support holes. The two ends of the rotating shaft 312 are respectively connected to the bearing end covers in the bearing support holes in the motor body 1 through dynamic seals. In addition, the bearing end cover and the rotating shaft 312 are hollow, and splines or key grooves are arranged in the hollow part of the rotating shaft 312 for fixedly connecting with the output shaft 32.

[0068] By arranging the bearing end cover on the rotating shaft 312, the distance from the cup-shaped blade 2 is relatively far, so the linear velocity of the rotating shaft 312 is reduced, and the service life of the dynamic seal is enhanced. A static seal is arranged between the motor base and the motor cover, enhancing the reliability, thereby improving the service life of the entire energy-saving fluid motor that can withstand high pressure and pressure pulsation.

[0069] As a preferred embodiment, the cup-shaped blade 2 includes a cup-shaped blade main body 21 and a connecting member 22. The cup-shaped blade main body 21 adopts a ladle-shaped, hemispherical structure or a multi-arc surface structure. The connecting member 22 is convexly connected to one side of the cup-shaped blade main body 21. A plurality of insertion slots for inserting the connecting member 22 are circumferentially arranged on the circumferential end surface of the wheel disc 311. The connecting member 22 is connected with insertion locking devices on both sides in the axial direction. The connecting member 22 is axially limited through the insertion locking devices, so that after the connecting member 22 is locked and connected with the turntable, the cup-shaped blade 2 is connected to the circumference of the turntable.

[0070] The connecting member 22 is of a columnar structure. The connecting member 22 is convexly connected to both side surfaces of the cup-shaped blade main body 21 in the axial direction, so that the connecting member 22 can be installed in the insertion slot and both ends of the connecting member 22 can extend out of the insertion slot, facilitating the installation of both ends of the connecting member 22 with the insertion locking devices. The length of the connecting member 22 is greater than the thickness of the cup-shaped blade main body 21 in the axial direction, so as to realize a reserved installation position for the insertion locking devices.

[0071] The insertion locking device can adopt the method of spring pins or buckles, etc. When using spring pins, through holes penetrating the connecting member 22 are radially opened at both ends of the connecting member 22 in the axial direction, and then the spring pins are respectively inserted and connected into the through holes. After the spring buckles of the spring pins are buckled, the movement of the connecting member 22 in the axial direction in the insertion slot is restricted. Thus, the axial limit of the connecting member 22 is realized through the spring pins arranged at both ends of the connecting member 22, further strengthening the connection tightness between the connecting member 22 and the wheel disc 311. The cup-shaped blade 2 will not break away from the wheel disc 311 when rotating with the wheel disc 311, improving the connection strength.

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

[0073] Through the arrangement of the arc-connected connecting end and the connecting member 22 body with an annular structure, the connecting member 22 can be connected to the circular insertion groove, and on the other side of the connecting member 22, the cup-shaped blade 2 forms a certain angle with the radial direction of the wheel disc 311, so that the cup-shaped blade 2 surrounds the wheel disc 311 in a ring shape.

[0074] As 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 communicated with the second fluid section 82, the first fluid section 81 is communicated with the recovery channel, and the second fluid section 82 is communicated with the accommodation cavity or the oil outlet channel 5.

[0075] Furthermore, the first fluid section 81 is vertically connected to the shock wave channel 6; alternatively, the first fluid section 81 is obliquely connected to the shock wave channel 6.

[0076] As a preferred embodiment, the flow assistance channel 9 includes a third fluid section 91 and a fourth fluid section 92; the third fluid section 91 is communicated with the fourth fluid section 92, the third fluid section 91 is communicated with the shock wave channel 6, and the fourth fluid section 92 is communicated with the accommodation cavity or the oil inlet channel 4.

[0077] As a preferred embodiment, the motor of the present application resistant to large pulsating flow further includes a sensor, which is arranged on the motor cover outside the rotary cavity of the motor body 1 accommodating the cup-shaped blade 2 and / or outside the motor seat; the outlet flow volume V of the oil outlet channel is measured by the sensor 1i and the time length T required for the outflow 1i , the number n of cup-shaped blades passed through 1i , the average time length t passed 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 is the flow rate passing through the cup-shaped blade each time;

[0080] The displacement q passing through the cup-shaped blade each time can be obtained1i , and the average displacement of the motor is obtained by taking the average value of the displacement measured each time as:

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

[0082] In the formula, q is the average displacement of the motor, q 11 is the displacement passing through the cup-shaped blade for the first time, q 12 is the displacement passing through the cup-shaped blade for the second time, q 1i is the displacement passing through the cup-shaped blade for the i-th time, and the number of times i ≥ 3.

[0083] It should be noted that there can be various choices for the number of cup-shaped blades evenly distributed on the circumference of the wheel disc. Preferably, the number n 1i of cup-shaped blades fully inserted into the insertion slots is the standard specification. In addition to being fully inserted into the insertion slots, the cup-shaped blades can also not be fully inserted into the insertion slots. At this time, the number of cup-shaped blades that can be evenly distributed is n ji , but j cannot be less than 3. At least 3 cup-shaped blades 2 can be retained in the accommodating cavity between the oil outlet channel 5 and the oil inlet channel 4 to ensure stable torque and full energy utilization.

[0084] In the present application, those parts not described can be implemented by adopting or referring to the existing technologies.

[0085] Each embodiment in this specification is described in a progressive manner. For the same or similar parts among the embodiments, reference can be made to each other. The key points of each embodiment are to illustrate the differences from other embodiments.

[0086] The above are only the embodiments of the present application and are not used to limit the present application. For those skilled in the art, various changes and modifications can be made to the present application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included within the scope of the claims of the present application.

Claims

1. An energy-saving fluid motor capable of withstanding high pressure and pressure pulsation, characterized in that: It includes a motor body, cup-shaped blades, an output wheel shaft and a shock wave recoverer; a plurality of cup-shaped blades are connected to the outer periphery of the output wheel shaft; the motor body includes a symmetrically connected motor cover and a motor seat, a housing cavity for accommodating the cup-shaped blades and the output wheel shaft is formed in the motor cover and the motor seat, and the output wheel shaft transmits power outward through the bearing support on the motor cover and the motor seat; the motor body is also provided with an oil inlet and an oil outlet, the axis of the oil inlet is tangent to the center line of the rotation trajectory of the cup-shaped blade, the cup mouth of the cup-shaped blade at the tangent point faces the oil inlet, and a shock wave channel is arranged perpendicular to the axis of the oil inlet or within an angle of 120°; a one-way valve is arranged 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; The two sides of the bottom of the shock wave channel are connected with a flow-assisting channel and a braking channel respectively; the outlet of the flow-assisting 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 therein is consistent with the rotation direction of the cup-shaped blade or hits the top; the flow-assisting channel is connected with a flow-assisting control valve, and the braking channel is connected with a braking control valve; The large pulsating flow passes through the shock wave recoverer at the bottom of the shock wave channel, and then the pressure is increased and stabilized before entering the flow-aiding channel and the brake channel on both sides; when the flow-aiding control valve is opened, the cup-shaped blades drive the output wheel shaft to rotate under the impact of the incoming flow in the oil inlet channel and the flow-aiding channel; when the brake control valve is opened, the brake channel sends the pulsating flow after pressure increase and stabilization to the cup-shaped blades, hindering the rotation of the cup-shaped blades, so that the output wheel shaft can achieve flexible semi-braking under the action of opposite torque.

2. An energy-saving fluid motor capable of withstanding high pressure and pressure pulsation as claimed in claim 1, characterized in that: The axis of the oil outlet passage is tangent to the center line of the rotation track of the cup-shaped blade, and the cup bottom of the cup-shaped blade at the tangent point faces the oil outlet passage; the axis lines of the oil outlet passage and the oil inlet passage are collinear or non-collinear; At least three cup-shaped blades can be retained in the accommodation cavity between the oil outlet and the oil inlet to ensure stable torque and full energy utilization; When the center lines of the oil outlet passage and the oil inlet passage are colinear, the oil outlet passage and the accommodating chamber may adopt a snail shell structure.

3. An energy-saving fluid motor capable of withstanding high pressure and pressure pulsation as claimed in claim 2, characterized in that: The angle between the flow-assisting 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-assisting control valve is opened, the pressure fluid in the flow-assisting channel assists the oil inlet channel to increase the rotational energy input to the cup blade; when the brake control valve is opened and the flow-assisting control valve is closed, the pressure fluid in the brake channel hinders the outflow of the oil outlet channel or hinders the rotation of the cup blade.

4. An energy-saving fluid motor capable of withstanding high pressure and pressure pulsation as claimed in claim 1, characterized in that: The output wheel shaft includes an output wheel shaft body and an output shaft; the output shaft body is connected to the motor body; the output wheel shaft body includes a wheel disc and a rotating shaft, the wheel disc is circumferentially connected with a plurality of cup-shaped blades, the rotating shaft is fixedly connected to the wheel disc, and both ends of the rotating shaft are respectively connected to 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 rotating shaft, and the output shaft is fixedly connected to the rotating shaft through a key or a spline.

5. An energy-saving fluid motor capable of withstanding high pressure and pressure pulsation as claimed in claim 4, characterized in that: The cup-shaped blade includes a cup-shaped blade body and a connecting piece; the cup-shaped blade body adopts a scoop-shaped, hemispherical structure or a multi-arc structure; the connecting piece is protruding and connected to one side of the cup-shaped blade body; a plurality of plug-in grooves for plugging in the connecting piece are opened in the circumferential direction on the circumferential end surface of the wheel disc, and the connecting piece is connected with plug-in locking devices on both sides along the axial direction. The plug-in locking devices are used to limit the connecting piece in the axial direction, so that after the connecting piece is locked and connected to the turntable, the cup-shaped blade is connected to the circumference of the turntable.

6. An energy-saving fluid motor capable of withstanding high pressure and pressure pulsation as claimed in claim 5, characterized in that: The connector comprises a connector body with an annular structure and a connecting section connected to the connector body in an arc shape; one end of the connecting section is tangentially connected to the outer periphery of the connector body, and the other end of the connecting section is tangentially connected to the cup-shaped blade.

7. An energy-saving fluid motor capable of withstanding high pressure and pressure pulsation as claimed in claim 1, characterized in that: The brake 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 chamber or the oil outlet.

8. An energy-saving fluid motor capable of withstanding high pressure and pressure pulsation as claimed in claim 7, characterized in that: The first fluid section is vertically connected to the shock wave channel; or, the first fluid section is obliquely connected to the shock wave channel.

9. An energy-saving fluid motor capable of withstanding high pressure and pressure pulsation as claimed in claim 1, characterized in that: The flow-aiding channel includes a third fluid segment and a fourth fluid segment; the third fluid segment is connected to the fourth fluid segment, the third fluid segment is connected to the shock wave channel, and the fourth fluid segment is connected to the accommodating cavity or to the oil inlet channel.

10. An energy-saving fluid motor capable of withstanding high pressure and pressure pulsation as claimed in claim 1, characterized in that: Also included is a sensor, which is disposed on the motor cover and / or the outside of the motor seat outside the cavity of the motor body that accommodates the rotation of the cup-shaped blades; The outlet flow volume V of the oil outlet is measured by the sensor 1i and the time required for outflow T 1i 、Number of cup-shaped blades passing through n 1i , the average time t between two adjacent cup-shaped leaves 1i , through the formula: q 1i =Q 1i / (n 1i ×t 1i )=(V 1i / T 1i ) / (n 1i ×t 1i ) In the formula, Q 1i is the flow rate passing through the cup blade each time; The displacement q per cup blade can be obtained 1i And take the average displacement of each measurement to get the average displacement q of the motor as: q=(q 11 +q 12+...+ q 1i ) / i Where q is the average displacement of the motor, q 11 is the displacement through the cup blades for the first time, q 12 is the displacement through the cup blades for the second time, q 1i is the displacement through the cup blade for the i-th time, i ≥ 3.

Images