Emulsion motor and hydraulic system

Abstract

The invention relates to the technical field of hydraulic elements, and provides an emulsion motor and a hydraulic system. In the emulsion motor, a non-circular planetary gear pair is adopted as a core transmission mechanism of a hydraulic driving assembly, the working principle of the non-circular planetary gear pair is insensitive to the lubricity and viscosity of emulsion, and internal leakage is substantially reduced, so that the inherent defects that a traditional motor is low in energy conversion efficiency in an emulsion medium and severe in operation heating are overcome; high-efficiency and low-heat-consumption large-torque stable output is achieved, and the harsh requirement for long-time continuous operation of heavy equipment can be met. Secondly, an actuating mechanism of the brake assembly is set to directly respond to a liquid pressure signal, deep cooperation of hydraulic driving and braking functions on control logic is achieved, the problems that in a traditional system, driving and braking serve as an independent system, response is not synchronous, and control is not accurate are solved, and the system reliability is improved. And the working reliability, safety and control precision of the whole machine are greatly improved.

Description

Technical Field

[0001] This invention relates to the field of hydraulic components, and more particularly to an emulsion motor and hydraulic system. Background Technology

[0002] In harsh environments with strict explosion-proof requirements, such as underground coal mines, hydraulic power components must use non-flammable emulsions or water as the working medium. However, hydraulic motors manufactured using traditional structures (such as internally curved radial piston motors) have inherent technical bottlenecks: when operating in emulsion environments, they generally suffer from severe internal leakage, low energy conversion efficiency, high heat generation, and poor rust resistance of internal parts, leading to a significant decrease in output torque and service life, making it difficult to meet the stringent requirements of heavy equipment for long-term, high-torque continuous operation. At the same time, the drive system of such equipment has extremely high safety requirements, needing rapid and reliable braking capabilities. However, in existing technologies, hydraulic drive and braking control are often designed as two relatively independent systems. The deficiencies in their dynamic response and coordinated control may affect the reliability, safety, and control accuracy of the entire machine. Summary of the Invention

[0003] To address the aforementioned technical problems, the present invention provides an emulsion motor and a hydraulic system.

[0004] A first aspect of the present invention provides an emulsion motor, comprising: a motor housing having an internal accommodating cavity; a hydraulic drive assembly disposed within the accommodating cavity, comprising: a non-circular planetary gear pair, a front distribution plate, a rear distribution plate, and a rotating shaft, wherein the front distribution plate and the rear distribution plate are respectively disposed on opposite axial sides of the non-circular planetary gear pair, the front distribution plate, the rear distribution plate, and the non-circular planetary gear pair together constitute a plurality of variable-volume sealed working cavities, the rotating shaft axially penetrates the front distribution plate, the non-circular planetary gear pair, and the rear distribution plate, and is connected to the non-circular planetary gear pair, wherein the two ends of the rotating shaft are an output end and a braking end, respectively; and a braking assembly comprising: a friction assembly and an actuation mechanism, wherein the actuation mechanism is configured to: drive the friction assembly to separate from the braking end in response to liquid pressure; and drive the friction assembly to engage with the braking end in response to the release of liquid pressure.

[0005] According to the present invention, an emulsion motor is provided, wherein the non-circular planetary gear pair includes: a non-circular internal gear ring connected to the motor housing; a non-circular sun gear coaxially disposed on the inner ring of the non-circular internal gear ring and connected to the rotating shaft; and a plurality of planet gears respectively meshing between the non-circular sun gear and the non-circular internal gear ring.

[0006] According to the present invention, the pitch curve of the non-circular internal gear ring is an equilateral closed curve; the pitch curve of the non-circular sun gear is a hexagonal closed curve; and the number of planetary gears is 14.

[0007] According to the emulsion motor provided by the present invention, the pitch curves of the non-circular internal gear ring and the non-circular sun gear both adopt a double circular arc segment configuration, and are fitted with sixth-order and fifth-order Fourier equations respectively, so as to maximize the accuracy of pitch curve modeling and minimize the computational load; the ratio of the number of teeth of the non-circular internal gear ring and the non-circular sun gear in each cycle of their pitch curves to the number of teeth of the planetary gears is 1.1.

[0008] According to the present invention, the tooth profiles of the non-circular internal gear ring and the non-circular sun gear are integrated conjugate tooth profiles generated by the envelope of the trajectory of each point on the tooth profile when the tool pitch circle rolls purely around the center of its respective pitch curve.

[0009] According to an emulsion motor provided by the present invention, the hydraulic drive assembly further includes: a front end cover connected to the motor housing and located outside the front distribution plate; a rear end cover connected to the motor housing and located outside the rear distribution plate; the rotating shaft passes through the front end cover, the front distribution plate, the non-circular planetary gear pair and the rear distribution plate in sequence, and is rotatably supported on the front end cover and the rear end cover via bearings.

[0010] According to an emulsion motor provided by the present invention, the braking assembly further includes: a brake housing connected to the motor housing; a brake end cap connected to the brake housing, the two forming a brake cavity; the friction assembly includes: a static friction plate connected to the inner wall of the brake housing; and a dynamic friction plate connected to the rotating shaft.

[0011] The actuation mechanism includes: a pressure plate, which is axially slidably disposed in the braking cavity and located between the friction assembly and the braking end cover; and an elastic element, located between the pressure plate and the braking end cover.

[0012] The brake housing has a brake fluid port that communicates with the brake cavity. When pressurized fluid is introduced, it can drive the pressure plate to compress the elastic element, thereby separating the dynamic friction plate from the static friction plate. When the fluid pressure is released, the elastic element drives the pressure plate to press the dynamic friction plate and the static friction plate together.

[0013] According to an emulsion motor provided by the present invention, a plurality of flow guiding structures are formed on the end face of the pressure plate facing the friction assembly, extending radially from the corresponding region of the brake fluid port away from the corresponding region of the pressure plate.

[0014] According to an emulsion motor provided by the present invention, a limiting groove is formed on the end face of the pressure plate near the elastic member, and the elastic member is at least partially accommodated in the limiting groove.

[0015] A second aspect of the invention provides a hydraulic system comprising an emulsion motor as described above.

[0016] The emulsion motor provided by this invention includes a motor housing, a hydraulic drive assembly, and a braking assembly. A receiving cavity is formed within the motor housing, and the hydraulic drive assembly is disposed within the receiving cavity. The hydraulic drive assembly includes a non-circular planetary gear pair, a front distributor plate, a rear distributor plate, and a rotating shaft. The front and rear distributor plates are respectively positioned on opposite axial sides of the non-circular planetary gear pair, collectively forming multiple variable-volume sealed working chambers. The rotating shaft axially passes through the front distributor plate, the non-circular planetary gear pair, and the rear distributor plate, and is connected to the non-circular planetary gear pair. The two ends of the rotating shaft are an output end and a braking end, respectively. The output end is a torque output section. The braking end is used to separate from or engage with the braking assembly. Specifically, the braking assembly includes a friction assembly and an actuation mechanism. The actuation mechanism is configured to drive the friction assembly to separate from the braking end in response to liquid pressure; and to drive the friction assembly to engage with the braking end in response to the release of liquid pressure.

[0017] The motor begins operation when pressurized fluid for both driving and braking is present. Driving fluid enters the motor housing's accommodating chamber, is distributed via the front distribution plate, and flows into multiple variable-volume sealed working chambers comprised of the front and rear distribution plates and a non-circular planetary gear pair. This drives the non-circular planetary gear pair, rotating the shaft and outputting torque. At this point, the driving fluid becomes low-pressure fluid, flowing back to the reservoir via the rear distribution plate and the accommodating chambers, ultimately exiting through another port on the motor housing. Simultaneously, brake fluid acts on the brake assembly's actuation mechanism. Responding to this pressure, the actuation mechanism drives the friction assembly to disengage from the brake end of the shaft, releasing the brake. When the pressure of both the driving and brake fluids is cut off, the hydraulic drive assembly stops outputting power. Simultaneously, the brake assembly's actuation mechanism, due to the pressure release, drives the friction assembly to engage with the brake end, generating braking torque to quickly stop and lock the shaft.

[0018] As described above, firstly, this technical solution uses a non-circular planetary gear pair as the core transmission mechanism of the hydraulic drive assembly. Its working principle is insensitive to the lubricity and viscosity of the emulsion, significantly reducing internal leakage. This overcomes the inherent defects of traditional motors in emulsion media, such as low energy conversion efficiency, severe heat generation, and poor reliability, achieving high-efficiency, low-heat-consumption, and stable high-torque output, meeting the stringent requirements of heavy equipment operating continuously for extended periods. Secondly, by setting the actuation mechanism of the braking assembly to directly respond to the liquid pressure signal, deep synergy between the hydraulic drive and braking functions in the control logic is achieved. This solves the problems of asynchronous response and inaccurate control in traditional systems where drive and braking are independent systems, greatly improving the reliability, safety, and control precision of the entire machine.

[0019] Furthermore, in the hydraulic systems provided by this invention, since they all include the emulsion motors described above, they also possess the advantages described above. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0021] Figure 1 This is a schematic diagram of the structure of the emulsion motor provided by the present invention.

[0022] Figure 2 This is a schematic diagram of the structure of the non-circular planetary gear pair in the emulsion motor provided by the present invention.

[0023] Figure 3 This is a schematic diagram of the front distribution plate in the emulsion motor provided by the present invention.

[0024] Figure 4 yes Figure 3 Schematic diagram of the AA section structure.

[0025] Figure 5 yes Figure 4 A schematic diagram of the structure along direction A; Figure 6 This is a schematic diagram of the structure of the rear distribution plate in the emulsion motor provided by the present invention.

[0026] Figure 7 yes Figure 6 Schematic diagram of the cross-sectional structure of the middle BB.

[0027] Figure 8 yes Figure 7A schematic diagram of the B-direction structure.

[0028] Figure 9 This is a schematic diagram of the pressure plate of the emulsion motor provided by the present invention.

[0029] Reference numerals: 100, Motor housing; 210, Non-circular planetary gear pair; 211, Non-circular internal gear ring; 212, Non-circular sun gear; 213, Planetary gear; 220, Front distributor plate; 230, Rear distributor plate; 240, Shaft; 250, Front end cover; 260, Rear end cover; 310, Brake housing; 311, Brake fluid port; 320, Brake end cover; 330, Static friction plate; 340, Dynamic friction plate; 350, Pressure plate; 351, Flow guiding structure; 352, Limiting groove; 360, Elastic element. Detailed Implementation

[0030] The embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and should not be construed as limiting the scope of the invention.

[0031] In the description of the embodiments of the present invention, it should be noted that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of the present invention 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. Therefore, they should not be construed as limitations on the embodiments of the present invention. In addition, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0032] In the description of the embodiments of the present invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of the present invention based on the specific circumstances.

[0033] In embodiments of the present invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0034] In the description of this specification, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Furthermore, without contradiction, those skilled in the art can combine and integrate different embodiments or examples and features of different embodiments or examples described in this specification to make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer. The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0035] The following is combined Figures 1 to 9 An emulsion motor and hydraulic system provided in an embodiment of the present invention will be described. It should be understood that the following description is merely an illustrative embodiment of the present invention and does not constitute any particular limitation on the present invention.

[0036] An embodiment of the first aspect of the present invention provides an emulsion motor, such as... Figures 1 to 8As shown, the assembly includes: a motor housing 100 with an internal accommodating cavity; a hydraulic drive assembly disposed within the accommodating cavity, comprising: a non-circular planetary gear pair 210, a front distributor plate 220, a rear distributor plate 230, and a rotating shaft 240. The front distributor plate 220 and the rear distributor plate 230 are respectively disposed on opposite axial sides of the non-circular planetary gear pair 210. The front distributor plate 220, the rear distributor plate 230, and the non-circular planetary gear pair 210 together constitute multiple variable-volume sealed working cavities. The rotating shaft 240 axially penetrates the front distributor plate 220, the non-circular planetary gear pair 210, and the rear distributor plate 230, and is connected to the non-circular planetary gear pair 210. The two ends of the rotating shaft 240 are an output end and a braking end, respectively; and a braking assembly comprising: a friction assembly and an actuation mechanism. The actuation mechanism is configured to: drive the friction assembly to separate from the braking end in response to liquid pressure; and drive the friction assembly to engage with the braking end in response to the release of liquid pressure.

[0037] The emulsion motor provided by this invention includes a motor housing 100, a hydraulic drive assembly, and a braking assembly. A receiving cavity is formed within the motor housing 100, and the hydraulic drive assembly is disposed within the receiving cavity. The hydraulic drive assembly includes a non-circular planetary gear pair 210, a front distributor plate 220, a rear distributor plate 230, and a rotating shaft 240. The front distributor plate 220 and the rear distributor plate 230 are respectively positioned on opposite axial sides of the non-circular planetary gear pair 210, together forming multiple variable-volume sealed working chambers. The rotating shaft 240 axially passes through the front distributor plate 220, the non-circular planetary gear pair 210, and the rear distributor plate 230, and is connected to the non-circular planetary gear pair 210. The two ends of the rotating shaft 240 are an output end and a braking end, respectively. The output end is a torque output section. The braking end is used for separation or engagement with the braking assembly. Specifically, the braking assembly includes a friction assembly and an actuation mechanism. The actuation mechanism is configured to disengage the friction assembly from the braking end in response to fluid pressure; and to engage the friction assembly with the braking end in response to release of fluid pressure.

[0038] The motor begins operation when pressurized fluid for both driving and braking is present. Drive fluid enters the receiving cavity of the motor housing 100, is distributed via the front distribution plate 220, and flows into multiple variable-volume sealed working chambers formed by the front distribution plate 220, the rear distribution plate 230, and the non-circular planetary gear pair 210. This drives the non-circular planetary gear pair 210, thereby driving the rotating shaft 240 to rotate and output torque from its output end. At this time, the drive fluid becomes a low-pressure fluid, flowing back to the reservoir via the rear distribution plate 230 and the receiving cavity, and finally through another port on the motor housing 100. Simultaneously, brake fluid acts on the actuation mechanism of the brake assembly. Responding to this pressure, the actuation mechanism drives the friction assembly to separate from the brake end of the rotating shaft 240, releasing the brake. When the pressure of the drive fluid and brake fluid is cut off, the hydraulic drive assembly stops outputting power. Simultaneously, the actuation mechanism of the brake assembly, due to the release of pressure, drives the friction assembly to engage with the brake end, generating braking torque to quickly stop and lock the rotating shaft 240.

[0039] As described above, firstly, this technical solution uses a non-circular planetary gear pair 210 as the core transmission mechanism of the hydraulic drive assembly. Its working principle is insensitive to the lubricity and viscosity of the emulsion, significantly reducing internal leakage. This overcomes the inherent defects of traditional motors in emulsion media, such as low energy conversion efficiency, severe heat generation, and poor reliability, achieving high-efficiency, low-heat-consumption, and stable high-torque output, meeting the stringent requirements of long-term continuous operation of heavy equipment. Secondly, by setting the actuation mechanism of the braking assembly to directly respond to the liquid pressure signal, deep synergy between the hydraulic drive and braking functions in the control logic is achieved. This solves the problems of asynchronous response and inaccurate control in traditional systems where drive and braking are independent systems, greatly improving the reliability, safety, and control precision of the entire machine.

[0040] In one embodiment of the present invention, the non-circular planetary gear pair 210 includes: a non-circular internal gear ring 211, which is connected to the motor housing 100; a non-circular sun gear 212, which is coaxially disposed on the inner ring of the non-circular internal gear ring 211 and connected to the rotating shaft 240; and a plurality of planet gears 213.

[0041] Furthermore, in one embodiment of the present invention, the hydraulic drive assembly further includes: a front cover 250, connected to the motor housing 100 and located outside the front distributor plate 220; and a rear cover 260, connected to the motor housing 100 and located outside the rear distributor plate 230.

[0042] The rotating shaft 240 passes through the front cover 250, the front distribution plate 220, the non-circular planetary gear pair 210 and the rear distribution plate 230 in sequence, and is rotatably supported on the front cover 250 and the rear cover 260 via bearings.

[0043] Furthermore, in one embodiment of the present invention, the braking assembly further includes: a brake housing 310 connected to the motor housing 100; and a brake end cap 320 connected to the brake housing 310, the two forming a brake chamber.

[0044] The friction assembly includes: a static friction plate 330, which is connected to the inner wall of the brake housing 310; and a dynamic friction plate 340, which is connected to the rotating shaft 240.

[0045] The actuation mechanism includes: a pressure plate 350, which is axially slidably disposed in the braking cavity and located between the friction assembly and the brake end cover 320; and an elastic element 360, which is located between the pressure plate 350 and the brake end cover 320.

[0046] The brake housing 310 has a brake fluid port 311 that communicates with the brake chamber. When pressurized fluid is introduced, it can drive the pressure plate 350 to compress the elastic element 360, so as to separate the moving friction plate 340 from the stationary friction plate 330. When the fluid pressure is released, the elastic element 360 drives the pressure plate 350 to press the moving friction plate 340 and the stationary friction plate 330 together.

[0047] Specifically, such as Figures 1 to 8 As shown, a cylindrical accommodating cavity is machined inside the motor housing 100. A front cover 250 and a rear cover 260 are fixedly connected to both ends of the motor housing 100 along its axial direction, respectively. The front cover 250, the rear cover 260, and the motor housing 100 together form a sealed main housing structure.

[0048] The hydraulic drive assembly is housed within the accommodating cavity of the motor housing 100 and is the power core of the motor. It includes: a non-circular planetary gear pair 210, a front distributor plate 220, a rear distributor plate 230, and a rotating shaft 240.

[0049] A rotating shaft 240 passes through the front cover 250, the receiving cavity of the motor housing 100, and the rear cover 260. The rotating shaft 240 is rotatably supported on the front cover 250 and the rear cover 260 by a first bearing and a second bearing, respectively, ensuring the smoothness and coaxiality of the rotation of the rotating shaft 240. One end of the rotating shaft 240 serves as an output end, used to connect to and drive the working mechanism externally, while the other end serves as a braking end, extending into the braking assembly described later.

[0050] The non-circular planetary gear pair 210 includes a non-circular internal gear ring 211, a non-circular sun gear 212, and multiple planet gears 213. The non-circular internal gear ring 211 is connected to the inner wall of the motor housing 100 via a gear ring pin, preventing it from rotating. The non-circular sun gear 212 is coaxially disposed within the inner ring of the non-circular internal gear ring 211, and its central hole is circumferentially fixed to the rotating shaft 240 via a coupling pin, thereby transmitting torque to the rotating shaft 240. Multiple planet gears 213 simultaneously mesh with the non-circular internal gear ring 211 and the non-circular sun gear 212. There are axial clearances between the two ends of these planet gears 213 and the front distribution plate 220 and the rear distribution plate 230. When the driving fluid enters the variable-volume sealed working chamber, it also enters the aforementioned axial clearances, forming a pressure laminar flow, supporting the rotation of the planet gears 213 and the non-circular sun gear 212 and preventing frictional wear on their end faces.

[0051] The front distribution plate 220 and the rear distribution plate 230 constitute the flow distribution system of the emulsion motor. The front distribution plate 220 and the rear distribution plate 230 are precisely aligned by locating pins and are respectively sealed tightly against the axial sides of the non-circular planetary gear pair 210. Together with the inner wall of the motor housing 100, they form the inlet chamber and the return chamber. Both the front distribution plate 220 and the rear distribution plate 230 are machined with precision flow distribution holes. For example, each of the front distribution plate 220 and the rear distribution plate 230 has eight circumferentially distributed flow distribution holes. The flow distribution holes on the front and rear distribution plates are staggered to match the time-varying size of the volume chamber, forming an efficient flow distribution. The cross-section of the flow distribution holes is L-shaped, and the L-shaped design of the flow distribution holes also minimizes the impact of the holes on the strength of the two flow distribution components.

[0052] Multiple sealed working cavities are formed by the tooth profile surfaces of two adjacent planetary gears 213, the tooth profile surface of the non-circular sun gear 212, the tooth profile surface of the non-circular internal gear ring 211, the inner end face of the front distribution plate 220, and the inner end face of the rear distribution plate 230. As the gears rotate, the volume of these working cavities changes periodically.

[0053] The braking assembly, the core component for achieving safety functions, is directly integrated into the rear end of the motor. Specifically, it includes: a brake housing 310, a brake end cover 320, a friction assembly, and an actuation mechanism. The brake housing 310 is bolted to the motor housing 100. The brake end cover 320 is bolted to the end of the brake housing 310. The brake housing 310, brake end cover 320, and rear end cover 260 together form a brake cavity. The brake end of the rotating shaft 240 extends into this brake cavity.

[0054] The friction assembly is housed within the brake cavity and includes a stationary friction plate 330 and a moving friction plate 340. The stationary friction plate 330 is circumferentially fixed by engaging a spline groove on the inner wall of the brake housing 310 via a spline (or lug) on ​​its outer edge. The moving friction plate 340 is circumferentially fixed by engaging a spline on the brake end of the rotating shaft 240 via a spline on its inner edge. Multiple moving friction plates 340 and stationary friction plates 330 are alternately stacked to form a multi-plate wet friction pair.

[0055] An actuation mechanism for controlling the engagement and disengagement of the friction assembly includes a pressure plate 350 and a disc spring. The pressure plate 350 is axially slidably disposed within the brake chamber and located between the friction assembly and the brake end cover 320. The disc spring is housed between the pressure plate 350 and the brake end cover 320, applying a continuous axial preload to the pressure plate 350, forcing the pressure plate 350 to press against the moving and stationary friction pads 330, thereby placing the brake assembly in a normally closed braking state. A brake fluid port 311 is provided on the brake housing 310, communicating with the brake control chamber formed by the pressure plate 350, the brake housing 310, and the friction assembly.

[0056] When the system requires the emulsion motor to operate, high-pressure emulsion is simultaneously supplied to both the hydraulic drive assembly and the brake assembly. The high-pressure emulsion enters the inlet chamber through the inlet on the motor housing 100, and then is precisely guided into the sealed working chamber, which is in the phase of decreasing volume, through the distribution holes on the front distribution plate 220. The high-pressure fluid acts on the tooth surfaces of the planetary gear 213, causing it to revolve around and rotate on its own axis around the non-circular sun gear 212. The rotation of the planetary gear 213 drives the non-circular sun gear 212 to rotate through meshing, thereby converting hydraulic energy into mechanical energy. The non-circular sun gear 212 transmits torque to the rotating shaft 240 through the coupling pin, causing it to rotate, and the power is ultimately stably output from the output end of the rotating shaft 240. Simultaneously, the high-pressure emulsion leading to the brake assembly enters the brake control chamber through the brake fluid port 311. The hydraulic pressure acts on the pressure plate 350, pushing it to overcome the preload of the disc spring and move towards the brake end cover 320. The retraction of the pressure plate 350 releases the axial clamping force on the friction pair composed of the moving friction plate 340 and the stationary friction plate 330, causing the moving and stationary friction plates 330 to separate, the brake to be completely released, and the rotating shaft 240 to rotate freely.

[0057] When the emulsion motor needs to be stopped, the pressurized fluid supply to the drive assembly and brake assembly is cut off. The pressure in the inlet chamber is lost, the sealed working chamber no longer receives high-pressure fluid replenishment, the driving force on the non-circular planetary gear pair 210 disappears, and the shaft 240 begins to decelerate. Simultaneously, the fluid pressure in the brake control chamber is rapidly unloaded. At this time, the compressed disc spring releases its stored elastic potential energy, driving the pressure plate 350 to move axially towards the friction assembly, axially pressing against the alternately stacked moving friction plates 340 and stationary friction plates 330. A large frictional torque is generated between the moving and stationary friction plates 330, which is transmitted through the spline to the braking end of the shaft 240, forcing the shaft 240 to stop quickly and reliably lock it in its current position. This braking process requires no external electrical signal control; it is an automatic mechanical action under pressure loss, achieving a "fail-safe" mode.

[0058] During the assembly process, the pre-assembly of the shaft 240 and bearing can be performed first: press the inner ring of the first bearing onto the corresponding shaft section at the front of the shaft 240, so that its front end face fits against the shaft shoulder of the shaft 240; then prepare the motor housing 100: press the outer ring of the first bearing into the bearing seat hole at the front end of the motor housing 100; assemble the front distributor plate 220 assembly: install each sealing ring and sealing retainer ring into the corresponding sealing groove on the front distributor plate 220; assemble the rear distributor plate 230 assembly: install each sealing ring and rotary seal into the corresponding sealing groove on the rear distributor plate 230; integrate the hydraulic drive assembly: insert the pre-assembled shaft 240 into the drive housing from the front - insert the locating pin into the motor housing. Insert the front distribution plate 220 with the assembled seal into the bottom of the inner cavity of the motor housing 100 from the rear, adjust its angle so that its pin hole is aligned with the positioning pin and installed in place; insert the non-circular internal gear ring 211 into the motor housing 100 and insert the connecting pin to connect and fix it to the front distribution plate 220 and the rear distribution plate 230; insert the coupling pin into the groove of the rotating shaft 240; insert the non-circular sun gear 212 and fix it to the rotating shaft 240 circumferentially through the coupling pin; install all the planet gears 213 in sequence so that they mesh with the non-circular internal gear ring 211 and the non-circular sun gear 212 at the same time; insert the rear distribution plate 230 with the assembled seal and align it with the connecting pin. Rear end support and housing closure: Install the rear end cover 260 and secure it with threaded fasteners to press the rear distributor plate 230, then sequentially install the second bearing and locking element for supporting the rear end of the rotating shaft 240; Integrated assembly of the brake assembly: Install the brake housing 310 onto the motor housing 100 and secure it with fasteners; sequentially install the necessary seals into the brake housing 310; alternately install multiple dynamic friction plates 340 (connected to the rotating shaft 240) and static friction plates 330 (connected to the brake housing 310); install the pressure plate 350, and then install the elastic element 360 (such as a disc spring); install the brake end cover 320 and secure it with fasteners to complete the encapsulation of the entire brake assembly and pre-compress the elastic element 360 to provide normally closed braking force for the brake assembly. Front end closure: Install the front end cover 250 and its seals onto the front end of the motor housing 100.

[0059] In one embodiment of the present invention, a plurality of flow guiding structures 351 are formed on the end face of the pressure plate 350 facing the friction assembly, extending radially from the corresponding region of the brake fluid port 311 away from the corresponding region of the pressure plate 350.

[0060] In other words, a special flow guiding structure 351 is formed on the end face of the pressure plate 350 facing the friction assembly. The core purpose of this flow guiding structure 351 is to guide the pressurized fluid into the brake control chamber from the brake fluid port 311 quickly and evenly to the hydraulic action end face of the pressure plate 350, so as to avoid the pressure plate 350 tilting or jamming due to the pressure build-up of the fluid on one side of the pressure plate 350 and the lag on the other side.

[0061] In another embodiment of the invention, such as Figure 9 As shown, the flow guiding structure 351 consists of multiple radially extending flow guiding sections. These flow guiding sections are grooves machined on the hydraulically actuated end face of the pressure plate 350. Specifically, it can be designed as four evenly distributed radial straight grooves, which are opposite each other in pairs, forming a cross-shaped flow guiding groove on the end face. When the high-pressure emulsion is injected from the brake fluid port 311, it can flow rapidly to the edge area of ​​the pressure plate 350 through the cross-shaped flow guiding groove, ensuring that the pressure can act on each area of ​​the hydraulically actuated end face of the pressure plate 350 almost synchronously, thereby generating a uniform, vertical axial thrust.

[0062] This ensures that the pressure plate 350 is subjected to uniform force throughout the entire movement, effectively preventing tilting caused by uneven force and abnormal friction between it and the inner wall of the brake housing 310, thus guaranteeing smooth and reliable brake release. Furthermore, the optimized flow channel allows for faster pressure build-up in the brake chamber, resulting in a quicker brake release response and improved overall machine efficiency. Additionally, it prevents uneven wear and jamming of the pressure plate 350, reducing wear on related parts and extending the service life of the brake assembly.

[0063] In some other embodiments, there may also be six or eight evenly distributed radial grooves, forming a denser radial flow channel, suitable for larger diameter pressure plates 350, so that the pressure distribution is more refined.

[0064] In one embodiment of the present invention, such as Figure 1 As shown, a limiting groove 352 is formed on the end face of the pressure plate 350 near the elastic member 360, and the elastic member 360 is at least partially accommodated within the limiting groove 352. This limits the maximum compression of the disc spring, preventing overload and damage, and effectively improving the fatigue life of the disc spring.

[0065] In one embodiment of the present invention, such as Figure 2 As shown, the pitch curve of the non-circular internal gear ring 211 is an equilateral closed curve; the pitch curve of the non-circular sun gear 212 is a hexagonal closed curve; and the number of planet gears 213 is 14.

[0066] In another embodiment of the present invention, the pitch curves of the non-circular internal gear ring 211 and the non-circular sun gear 212 both adopt a double circular arc configuration and are fitted with sixth-order and fifth-order Fourier equations, respectively, to maximize the accuracy of pitch curve modeling and minimize the computational load; the ratio of the number of teeth of the non-circular internal gear ring 211 and the non-circular sun gear 212 in each period of their pitch curves to the number of teeth of the planet gear 213 is 1.1.

[0067] Furthermore, in one embodiment of the present invention, the tooth profiles of the non-circular internal gear ring 211 and the non-circular sun gear 212 are integrated conjugate tooth profiles generated by the envelope of the trajectories of each point on the tooth profile of the tool when the tool pitch circle rolls purely around the center of its respective pitch curve.

[0068] Specifically, the non-circular planetary gear pair 210 is a specific type 6-8 non-circular planetary gear system. Its specific configuration parameters are as follows: the pitch curve of the non-circular internal gear ring 211 is an octagonal equilateral closed curve; the pitch curve of the non-circular sun gear 212 is a hexagonal equilateral closed curve; and the number of planet gears 213 is 14. Compared to traditional 4-6 type gear systems, this configuration results in a greater number of sealed working chambers formed by the gear pairs during the working cycle, meaning more units participate in work simultaneously and more meshing teeth, laying the foundation for larger and smoother torque output. Simultaneously, the pitch curves have been optimized: the pitch curves of both the non-circular internal gear ring 211 and the non-circular sun gear 212 use double circular arc segments as the basic constituent units. This design provides smooth initial conditions for subsequent high-precision fitting. In the polar coordinate system, the error between the fitted pitch curve model and the theoretical double-circular pitch curve is used as a direct criterion for judging the accuracy of the meshing pitch curve model. The root mean square and coefficient of determination of the aforementioned error reduction are used to evaluate the order of the Fourier equation used to fit the pitch curve to achieve the optimal combination of best fitting accuracy and minimum computational cost. Finally, the pitch curve of the non-circular sun gear is determined to be a fifth-order Fourier equation, and the pitch curve of the non-circular internal gear ring is determined to be a sixth-order Fourier equation, ensuring that the final pitch curve has extremely high smoothness and continuity, fundamentally avoiding rigid impact and vibration in the transmission. Based on the above optimized pitch curves, the final tooth profile of the non-circular internal gear ring 211 and the non-circular sun gear 212 is an integrated conjugate tooth profile generated by the envelope of the trajectory of each point on the tool tooth profile when the tool pitch circle rolls purely around the center of its respective pitch curve. The tooth profile can be accurately obtained through generating or wire cutting.

[0069] Compared to the traditional method of splicing tooth profiles at the transition point of the pitch curve, the method of this invention can define the shape of the entire tooth profile in one complete step. The generated tooth profile is integrated, continuous, and smooth, with no splicing errors.

[0070] The non-circular planetary gear pair 210 of this embodiment achieves the following technical effects: First, compared with the 4-6 type gear system, the 6-8 type configuration of this solution allows for a larger shaft hole size for the non-circular sun gear 212 under the same module, improving its structural strength and torque carrying capacity. Second, with a total of 14 working chambers, the theoretical output torque of the emulsion motor is significantly increased under the same emulsion input pressure and tooth width conditions. Due to the adoption of the double circular arc pitch curve fitted by the high-order Fourier equation of the 6-8 configuration, the instantaneous transmission ratio change of the gear transmission is smoother. In addition, the number of teeth meshing and disengaging simultaneously is increased, which greatly reduces meshing impact and vibration, resulting in smooth power output and significantly reduced noise level.

[0071] Meanwhile, the 6-8 type gear pair has a smaller length-to-diameter ratio. This means that, with the same output torque, the axial dimension of the hydraulic drive assembly is shorter, which is beneficial for the miniaturization and compact design of the entire machine. In addition, the integrated conjugate tooth profile generated by the rotation center envelope method around the pitch curve fundamentally eliminates tooth profile splicing errors and ensures meshing accuracy. The gear pair experiences uniform force during transmission and has minimal tooth surface wear, thereby significantly improving the reliability and service life of the entire hydraulic motor.

[0072] A second aspect of the present invention provides a hydraulic system including an emulsion motor as described above.

[0073] Furthermore, the hydraulic system provided by the present invention, since it includes the emulsion motor as described above, also possesses the advantages described above.

[0074] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. An emulsion motor, characterized in that, include: The motor housing (100) has an internal cavity; A hydraulic drive assembly is disposed within the accommodating cavity and includes: a non-circular planetary gear pair (210), a front distribution plate (220), a rear distribution plate (230), and a rotating shaft (240). The front distribution plate (220) and the rear distribution plate (230) are respectively disposed on both axial sides of the non-circular planetary gear pair (210). The front distribution plate (220), the rear distribution plate (230), and the non-circular planetary gear pair (210) together constitute multiple sealed working cavities with variable volumes. The rotating shaft (240) axially passes through the front distribution plate (220), the non-circular planetary gear pair (210), and the rear distribution plate (230) and is connected to the non-circular planetary gear pair (210). The two ends of the rotating shaft (240) are the output end and the braking end, respectively. A braking assembly comprising: a friction assembly and an actuation mechanism configured to: drive the friction assembly to separate from the braking end in response to liquid pressure; and drive the friction assembly to engage with the braking end in response to release of liquid pressure.

2. The emulsion motor according to claim 1, characterized in that, The non-circular planetary gear pair (210) includes: A non-circular internal gear ring (211) is connected to the motor housing (100); A non-circular sun gear (212) is coaxially disposed on the inner ring of the non-circular internal gear ring (211) and connected to the rotating shaft (240); Multiple planetary gears (213) are respectively meshed between the non-circular sun gear (212) and the non-circular internal gear ring (211).

3. The emulsion motor according to claim 2, characterized in that, The pitch curve of the non-circular internal gear ring (211) is an equilateral closed curve; the pitch curve of the non-circular sun gear (212) is a hexagonal closed curve; and the number of planet gears (213) is 14.

4. The emulsion motor according to claim 3, characterized in that, The pitch curves of the non-circular internal gear ring (211) and the non-circular sun gear (212) both adopt a double circular arc configuration and are fitted with sixth-order and fifth-order Fourier equations, respectively. The ratio of the number of teeth of the non-circular internal gear ring (211) and the non-circular sun gear (212) in each period of their pitch curves to the number of teeth of the planetary gear (213) is 1.

1.

5. The emulsion motor according to claim 4, characterized in that, The tooth profiles of the non-circular internal gear ring (211) and the non-circular sun gear (212) are integrated conjugate tooth profiles generated by the envelope of the trajectory of each point on the tooth profile when the tool pitch circle rolls purely around the center of its respective pitch curve.

6. The emulsion motor according to any one of claims 1 to 5, characterized in that, The hydraulic drive assembly also includes: The front cover (250) is connected to the motor housing (100) and is located on the outside of the front distributor plate (220); The rear end cover (260) is connected to the motor housing (100) and is located outside the rear distributor plate (230); The rotating shaft (240) passes through the front end cover (250), the front distribution plate (220), the non-circular planetary gear pair (210) and the rear distribution plate (230) in sequence, and is rotatably supported on the front end cover (250) and the rear end cover (260) via bearings.

7. The emulsion motor according to claim 6, characterized in that, The braking assembly also includes: The brake housing (310) is connected to the motor housing (100); The brake end cap (320) is connected to the brake housing (310), and the two together form a brake cavity; The friction assembly includes: The static friction plate (330) is connected to the inner wall of the brake housing (310); A moving friction plate (340) is connected to the rotating shaft (240); The actuation mechanism includes: The pressure plate (350) is axially slidably disposed in the brake cavity and located between the friction assembly and the brake end cover (320); An elastic element (360) is located between the pressure plate (350) and the brake end cap (320); The brake housing (310) has a brake fluid port (311) that communicates with the brake cavity. When pressurized liquid is introduced, it can drive the pressure plate (350) to compress the elastic element (360) so that the moving friction plate (340) and the stationary friction plate (330) are separated. When the liquid pressure is released, the elastic element (360) drives the pressure plate (350) to press the moving friction plate (340) and the stationary friction plate (330) together.

8. The emulsion motor according to claim 7, characterized in that, On the end face of the pressure plate (350) facing the friction assembly, a plurality of flow guiding structures (351) are formed extending radially from the corresponding region of the brake fluid port (311) away from the corresponding region of the brake fluid port (311).

9. The emulsion motor according to claim 7, characterized in that, The pressure plate (350) forms a limiting groove (352) on the end face near the elastic member (360), and the elastic member (360) is at least partially accommodated in the limiting groove (352).

10. A hydraulic system, characterized in that, Includes an emulsion motor as described in any one of claims 1 to 9.

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