Electric thruster and water-based moving apparatus

Abstract

An electric thruster, comprising a housing (10), a motor (20), a speed reducer assembly (30), a pump assembly (40), and a propeller (50). The housing is provided with a first cavity (10a) and a second cavity (10b) isolated from the first cavity, wherein the motor is disposed within the first cavity, and the speed reducer assembly and the pump assembly are disposed within the second cavity. The speed reducer assembly is coupled with a motor shaft (21). The pump assembly is also coupled with the motor shaft so as to pump liquid under the torque action of the motor shaft. The electric thruster cools and lubricates the speed reducer assembly, thus prolonging the service life of the speed reducer assembly and reducing the failure rate of the electric thruster. Further provided is a water-based moving apparatus (1000) comprising the electric thruster.

Description

Electric propulsion and water-movable equipment Technical Field

[0001] The present application relates to the field of marine propulsion, and in particular to an electric propeller and a movable device in water areas. Background Art

[0002] As the power demand for marine propulsion systems continues to grow, high-power motors are increasingly being used. As motor power increases, a speed reducer is required between the motor and propeller to increase propeller torque. Due to the mechanical coordination of the speed reducer's multiple rotating parts, it easily generates high temperatures and experiences significant frictional losses, resulting in a relatively short service life and an increased failure rate in marine propulsion systems.

[0003] Application Contents

[0004] The purpose of this application is to provide an electric propeller and a movable device in water area, which can increase the service life of the reducer and reduce the failure rate.

[0005] The present application provides an electric propulsion device, comprising:

[0006] The housing is provided with a first cavity and a second cavity isolated from the first cavity, wherein the first cavity is used to contain a cooling lubricating liquid, and the cooling lubricating liquid can exchange heat with water outside the housing through the housing;

[0007] a motor, disposed in the first cavity, the motor being provided with a motor shaft;

[0008] a reducer assembly, disposed in the second cavity and coupled to the motor shaft;

[0009] a pump assembly disposed in the second cavity, the pump assembly being coupled to the motor shaft to pump liquid under the action of the torque of the motor shaft, wherein the cooling lubricating liquid can be pumped away from the bottom of the first cavity under the pumping of the pump assembly and return to the bottom of the first cavity after at least partial contact with the reducer assembly;

[0010] A propeller is located outside the housing and is connected to the reducer assembly shaft.

[0011] The present application also provides a movable device in water area, comprising a water area carrier and the electric propeller as described above, wherein the electric propeller is connected to the water area carrier.

[0012] The electric propeller and the movable device in water provided by the present application are capable of cooling and lubricating the cooling lubricating liquid in the first cavity through the shell and exchanging heat with the water outside the shell, so that the cooling and lubricating liquid is cooled. Since the pump assembly is located in the second cavity, the pump assembly can complete the pumping of the liquid under the action of the torque of the motor shaft, and pump the cooling and lubricating liquid into contact with the reducer assembly to achieve cooling and lubrication of the reducer assembly. Stable cooling and lubrication of the reducer assembly can be achieved without the need for additional power structure and space. The electric propeller provided in the present application can achieve cooling and lubrication effects on the reducer assembly, increase the service life of the reducer assembly, and reduce the failure rate of the electric propeller. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying any creative work.

[0014] FIG1 is a cross-sectional schematic diagram of an electric propeller provided in an embodiment of the present application;

[0015] FIG2 is a schematic diagram of the structure of an electric propeller provided in an embodiment of the present application;

[0016] FIG3 is a second structural diagram of the electric propeller provided in an embodiment of the present application;

[0017] FIG4 is a third structural diagram of the electric propeller provided in an embodiment of the present application;

[0018] FIG5 is a schematic diagram of the installation structure of the pump assembly and the reducer assembly of the electric propeller provided in an embodiment of the present application;

[0019] Figure 6 is an enlarged view of point A in Figure 1;

[0020] FIG7 is a schematic diagram of a structure of a pump assembly of an electric propeller provided in an embodiment of the present application;

[0021] FIG8 is a second structural schematic diagram of a pump assembly of an electric propeller provided in an embodiment of the present application;

[0022] FIG9 is an exploded schematic diagram of a pump assembly of an electric propeller provided in an embodiment of the present application;

[0023] FIG10 is a schematic diagram of a movable device for use in water areas provided in an embodiment of the present application.

[0024] Explanation of Reference Numerals: 1000: Mobile Device for Water Areas; 100: Electric Propeller; 10: Housing; 10a: First Cavity; 10b: Second Cavity; 20: Motor; 21: Motor Shaft; 30: Reducer Assembly; 31: Torque Input Port; 311: Input Shaft; 312: Input Shaft Bearing; 313: Input Gear; 32: Torque Output Port; 321: Output Shaft; 322: Output Shaft Bearing; 323: Output Gear; 331: Intermediate Transmission Shaft; 332: Intermediate Shaft Bearing; 333a: First Intermediate Gear; 333b: Second Intermediate Gear; 40: Pump Assembly; 40a: Liquid Inlet Channel; 40b: Liquid Outlet Channel; 40c: First Liquid Outlet; 40d: Second Liquid Outlet; 41: Pump casing; 411: First housing; 412: Second housing; 41a: First bearing mounting slot; 41b: Second bearing mounting slot; 41c: Third bearing mounting slot; 41d: Fifth bearing mounting slot; 41e: Fourth bearing mounting slot; 41f: Sixth bearing mounting slot; 401: Rotor assembly; 42: First rotor shaft; 43: First rotor; 44: Second rotor; 45: Rotor limiting ring; 451: Mating boss; 46: Blocking member; 47: Liquid guide tube; 471: First liquid spray port; 472: Second liquid spray port; 473: Third liquid spray port; 48: Filter; 481: Magnetic member; 50: Propeller; 200: Water carrier. DETAILED DESCRIPTION

[0025] The following will be combined with the drawings in the embodiments of this application to clearly and completely describe the technical solutions in the embodiments of this application. Obviously, the embodiments described are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0026] It should be noted that all directional indications in the embodiments of the present application (such as up, down, left, right, front, back, etc.) are only used to explain the relative position relationship and movement status between the components in a certain specific posture. If the specific posture changes, the directional indication will also change accordingly.

[0027] It should also be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be an intervening element. When an element is referred to as being "connected to" another element, it may be directly connected to the other element or indirectly connected to the other element through an intervening element.

[0028] In addition, the descriptions of "first", "second", etc. in this application are for descriptive purposes only and should not be understood as indicating or implying their relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features defined as "first" or "second" may explicitly or implicitly include at least one of such features. In addition, the technical solutions between the various embodiments can be combined with each other, but this must be based on the fact that they can be implemented by ordinary technicians in this field. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such combination of technical solutions does not exist and is not within the scope of protection required by this application.

[0029] The following describes some embodiments of the present application in detail with reference to the accompanying drawings. In the absence of conflict, the following embodiments and features therein may be combined with each other.

[0030] As shown in FIG. 1 to FIG. 4 , an electric propeller 100 provided in an embodiment of the present application includes a housing 10 , a motor 20 , a reducer assembly 30 , a pump assembly 40 and a propeller 50 .

[0031] The housing 10 is provided with a first cavity 10a and a second cavity 10b isolated from the first cavity 10a. The second cavity 10b is used to hold a cooling lubricant, which can exchange heat with water outside the housing 10 through the housing 10. A motor 20 is disposed within the first cavity 10a and is provided with a motor shaft 21. A reducer assembly 30 is disposed within the second cavity 10b and is coupled to the motor shaft 21. A pump assembly 40 is disposed within the second cavity 10b and is coupled to the motor shaft 21 so as to pump liquid under the torque of the motor shaft 21. The cooling lubricant can be pumped from the bottom of the second cavity 10b by the pump assembly 40 and, after at least partial contact with the reducer assembly 30, return to the bottom of the second cavity 10b. A propeller 50 is located outside the housing 10 and is axially coupled to the reducer assembly 30.

[0032] It is understandable that the cooling lubricant can exchange heat with the water outside the shell 10 through the shell 10 to reduce the temperature of the cooling lubricant, so that the cooling lubricant can achieve cooling and lubrication at the same time when in contact with the reducer assembly 30. For example, overheating damage caused by dry friction can be avoided. The stable operation of the reducer assembly 30 is guaranteed. For example, when the electric propeller 100 is running underwater, the water outside the shell 10 can exchange heat with the shell 10, and then exchange heat with the cooling lubricant through the shell 10 to cool the cooling lubricant. Compared with other heat exchange methods, this method can directly utilize water, without the need for additional heat dissipation devices, and will not increase the weight of the electric propeller 100. It has low cost and excellent heat exchange effect.

[0033] It can be understood that the reducer can reduce the rotation speed of the motor shaft 21 and increase the torque output by the motor shaft 21 to ensure uniform and stable rotation of the propeller 50, increase the thrust of the propeller 50, and enable the electric propeller 100 to operate stably.

[0034] It is understood that since the motor 20 is disposed in the first cavity 10a, which is isolated from the second cavity 10b, the cooling lubricant does not come into contact with the motor 20. The cooling lubricant circulates within the second cavity 10b under the action of the pump assembly 40 to cool and lubricate the reducer assembly 30.

[0035] It is understandable that, since the pump assembly 40 can pump liquid under the torque of the motor shaft 21, there is no need to set up an additional power structure in the housing 10, which can ensure that the structure in the housing 10 is simple and will not increase the space in the housing 10. Under the pumping liquid of the pump assembly 40, the cooling lubricating liquid at the bottom of the second cavity 10b can be pumped to contact the reducer assembly 30 to cool and lubricate the reducer assembly 30 and ensure the stable operation of the reducer assembly 30. For example, the bearing shaft system in the reducer assembly 30 can be cooled and lubricated. In this way, the reducer assembly 30 provided in the present application does not need to be completely immersed in the cooling lubricating liquid to avoid excessive efficiency loss caused by stirring the oil. Of course, as needed, the reducer assembly 30 can also be partially immersed in the cooling lubricating liquid, so that the reducer assembly 30 can also stir the cooling lubricating liquid through its own rotation, and achieve cooling and lubrication by splashing.

[0036] It can be understood that since the pump assembly 40 is arranged in the second cavity 10b, only the input shaft 311 and the output shaft 321 of the reducer assembly 30 in the second cavity 10b are connected to the outside of the second cavity 10b. Therefore, there is no need to provide an interface for connecting to the pump assembly 40 on the cavity wall of the second cavity 10b. The structure is simple and easy to install and manufacture.

[0037] In the electric propeller 100 provided in the embodiment of the present application, the cooling lubricating liquid located in the first cavity 10a can be heat-exchanged with the water outside the housing 10 through the housing 10 to cool the cooling lubricating liquid. Since the pump assembly 40 is located in the second cavity 10b, the pump assembly 40 can complete the pumping of liquid under the action of the torque of the motor shaft 21, and pump the cooling lubricating liquid into contact with the reducer assembly 30 to achieve cooling and lubrication of the reducer assembly 30. Stable cooling and lubrication of the reducer assembly 30 can be achieved without the need for additional power structure and space. The electric propeller 100 provided in the present application can achieve cooling and lubrication effects on the reducer assembly 30, increase the service life of the reducer assembly 30, and reduce the failure rate of the electric propeller 100.

[0038] For example, the cooling lubricant is oil, which can achieve efficient heat exchange, and when it contacts the reducer assembly 30, it will not affect the operation of the reducer assembly 30 and can lubricate the reducer assembly 30. The cooling lubricant can also be other heat exchange fluids with lubricating effects, without limitation.

[0039] In the present application, the first cavity 10a and the second cavity 10b are both disposed in the underwater portion of the housing 10. The first cavity 10a is adjacent to the second cavity 10b, thereby reducing the distance between the motor 20 and the reducer assembly 30, facilitating the output of the rotational torque of the motor 20 to the reducer assembly 30 and the pump assembly 40, and improving the propulsion efficiency of the electric propeller 100. Since the first cavity 10a is disposed in the underwater portion of the housing 10, the motor 20 can directly exchange heat with the water outside the housing 10 through the housing 10, thereby cooling the motor 20 without requiring an additional cooling system to cool the motor 20, thereby reducing the volume and cost of the electric propeller 100.

[0040] As shown in Figures 1 to 4, in some embodiments, the reducer assembly 30 includes a torque input end 31 and a torque output end 32. The torque input end 31 receives torque from the motor 20, and the torque output end 32 outputs torque to the propeller 50. The pump assembly 40 is disposed at the torque input end 31 or the torque output end 32, or in the region between the torque input end 31 and the torque output end 32. It will be appreciated that the pump assembly 40 can be positioned at different locations within the reducer assembly 30 to pump fluid under different torque conditions. For example, when the pump assembly 40 is positioned at the torque input end 31, it can pump fluid under higher speeds and lower torques. When the pump assembly 40 is positioned at the torque output end 32, it can pump fluid under lower speeds and higher torques. When the pump assembly 40 is positioned between the torque input end 31 and the torque output end 32, it can pump fluid under moderate speeds and moderate torques. In this way, the pump assembly 40 can be positioned at different locations to improve the cooling and lubrication of the reducer assembly 30 according to different pumping requirements. In this embodiment, the pump assembly 40 is configured at different positions of the reducer assembly 30, and can pump liquid under the torque of the reducer assembly 30, so that the reducer assembly 30 and the pump assembly 40 can be more compactly arranged in the second cavity 10b without occupying additional space.

[0041] As shown in Figures 1 to 4, in some embodiments, the torque input end 31 includes an input shaft 311 capable of receiving torque from the motor 20, an input shaft bearing 312 engaged with the input shaft 311 and fixed within the housing 10, and an input gear 313 fixed to the input shaft 311. The torque output end 32 includes an output shaft 321 capable of outputting torque to the propeller 50, an output shaft bearing 322 engaged with the output shaft 321 and fixed within the housing 10, and an output gear 323 fixed to the output shaft 321. The output gear 323 receives rotational torque from the input gear 313. The input shaft bearing 312 can be used to support the input shaft 311, ensuring stable rotation of the input shaft 311, while the output shaft bearing 322 can be used to support the output shaft 321, ensuring stable rotation of the output shaft 321. During rotation, the input shaft 311 can drive the input gear 313 to rotate, and the input gear 313 transmits the rotational torque to the output gear 323, thereby driving the output shaft 321 to rotate. In this way, the torque can be transmitted to the propeller 50 through the speed reducer assembly 30 to achieve stable propulsion of the propeller 50.

[0042] For example, the axis of the motor shaft 21, the axis of the input shaft 311, and the axis of the output shaft 321 are located in the same straight line. The motor 20 and the reducer assembly 30 are arranged as close to the axial direction of the motor shaft 21 as possible, so as to extend along the axial direction of the motor shaft 21 corresponding to the bottom of the housing 10 of the electric propeller 100, so that the structure inside the electric propeller 100 is more reasonable and compact. Under this structure, the volume of the reducer assembly 30 is miniaturized, thereby reducing the volume of the underwater part of the electric propeller 100, that is, reducing the water-facing area of ​​the underwater part of the electric propeller 100 (the area blocked by the propeller 50 disk), reducing the water-facing resistance of the electric propeller 100, and improving the propulsion efficiency. Of course, as needed, the motor shaft 21, the input shaft 311, and the output shaft 321 may also be non-coaxial, as long as the torque transmission can be achieved.

[0043] As shown in Figures 1 and 2, in some embodiments, the cooling lubricant pumped by the pump assembly 40 flows through the input shaft 311. This cooling lubricant can cool or lubricate the input shaft 311, ensuring stable rotation of the input shaft 311. In this embodiment, the cooling lubricant pumped by the pump assembly 40 can flow through part or all of the input shaft 311. For example, the cooling lubricant pumped by the pump assembly 40 can flow through one end of the input shaft 311. It is understood that the pump fluid outlet of the pump assembly 40 can be positioned near one end of the input shaft 311, so that the cooling lubricant pumped by the pump assembly 40 flows through the input shaft 311. The pump fluid outlet of the pump assembly 40 can be positioned near one end of the input shaft 311 via a pipe or housing flow channel, and this embodiment is not limited thereto. Of course, the pump fluid outlet of the pump assembly 40 can also be positioned near either end of the input shaft 311, or near a location between the two ends of the input shaft 311, and this embodiment is not limited thereto.

[0044] As shown in Figures 1 and 2, in some embodiments, the cooling lubricant pumped by the pump assembly 40 flows through the input shaft bearing 312. It will be appreciated that input shaft bearings 312 are provided at both ends of the input shaft 311, meaning both input shaft bearings 312 can be cooled and lubricated by the cooling lubricant. Of course, as needed, the cooling lubricant pumped by the pump assembly 40 can be configured to cool and lubricate only one of the input shaft bearings 312 to increase cooling and lubrication efficiency, while the other input shaft bearing 312 can be cooled and lubricated by the cooling lubricant being rotated and stirred within the second cavity 10b. In this way, the cooling lubricant can cool or lubricate the input shaft bearings 312, ensuring stable rotation of the input shaft 311 relative to the input shaft bearings 312. In this embodiment, the cooling lubricant pumped by the pump assembly 40 can flow through one or more input shaft bearings 312. For example, the cooling lubricant pumped by the pump assembly 40 can flow through the input shaft bearing 312 at one end of the input shaft 311.

[0045] In some embodiments, the cooling lubricant pumped by the pump assembly 40 flows through the input gear 313. In this way, the cooling lubricant can cool or lubricate the input gear 313, ensuring that the input gear 313 can stably transmit torque. In this embodiment, the cooling lubricant pumped by the pump assembly 40 can flow through part or all of the input gear 313. For example, the cooling lubricant pumped by the pump assembly 40 can flow through the location where the input gear 313 meshes with other gears within the reducer assembly 30.

[0046] As shown in Figures 1 and 2, in some embodiments, the cooling lubricant pumped by the pump assembly 40 flows through the output shaft 321. This cooling lubricant can cool or lubricate the output shaft 321, ensuring stable rotation of the output shaft 321. In this embodiment, the cooling lubricant pumped by the pump assembly 40 can flow through part or all of the output shaft 321. For example, the cooling lubricant pumped by the pump assembly 40 can flow through one end of the output shaft 321. It is understood that the pump fluid outlet of the pump assembly 40 can be positioned near one end of the output shaft 321, so that the cooling lubricant pumped by the pump assembly 40 flows through the output shaft 321. The pump fluid outlet of the pump assembly 40 can be positioned near one end of the output shaft 321 via a pipe or housing flow channel, and this embodiment is not limited thereto. Of course, the pump fluid outlet of the pump assembly 40 can also be positioned near either end of the output shaft 321, or near a location between the two ends of the output shaft 321, and this embodiment is not limited thereto.

[0047] As shown in Figures 1 and 2, in some embodiments, the cooling lubricant pumped by the pump assembly 40 flows through the output shaft bearing 322. It will be appreciated that output shaft bearings 322 are provided at both ends of the output shaft 321, meaning that both output shaft bearings 322 can be cooled and lubricated by the cooling lubricant. Of course, as needed, the cooling lubricant pumped by the pump assembly 40 can be configured to cool and lubricate only one of the output shaft bearings 322 to increase cooling and lubrication efficiency, while the other output shaft bearing 322 can be cooled and lubricated by the cooling lubricant being rotated and stirred within the second cavity 10b. In this way, the cooling lubricant can cool or lubricate the output shaft bearings 322, ensuring stable rotation of the output shaft 321 relative to the output shaft bearings 322. In this embodiment, the cooling lubricant pumped by the pump assembly 40 can flow through one or more output shaft bearings 322. For example, the cooling lubricant pumped by the pump assembly 40 can flow through the output shaft bearing 322 at one end of the output shaft 321.

[0048] In some embodiments, the cooling lubricant pumped by the pump assembly 40 flows through the output gear 323. In this way, the cooling lubricant can cool or lubricate the output gear 323, ensuring that the output gear 323 can stably transmit torque. In this embodiment, the cooling lubricant pumped by the pump assembly 40 can flow through part or all of the output gear 323. For example, the cooling lubricant pumped by the pump assembly 40 can flow through the location where the output gear 323 meshes with other gears within the reducer assembly 30.

[0049] As shown in Figures 1 to 4, in some embodiments, the reducer assembly 30 further includes an intermediate transmission shaft 331 connected between the torque input end 31 and the torque output end 32, an intermediate shaft bearing 332 engaged with the intermediate transmission shaft 331 and fixed within the housing 10, and a first intermediate gear 333a and a second intermediate gear 333b fixed to the intermediate transmission shaft 331. The first intermediate gear 333a meshes with the input gear 313, and the second intermediate gear 333b meshes with the output gear 323. The outer diameter of the first intermediate gear 333a is larger than that of the second intermediate gear 333b. The first intermediate gear 333a and the second intermediate gear 333b rotate synchronously. The intermediate shaft bearing 332 supports the intermediate shaft, ensuring stable rotation. The rotation of the input shaft 311 drives the input gear 313, and the input gear 313 transmits the rotational torque to the first intermediate gear 333a. The first intermediate gear 333a drives the intermediate transmission shaft 331, which in turn drives the second intermediate gear 333b. The second intermediate gear 333b transmits the rotational torque to the output gear 323, thereby driving the output shaft 321 to rotate. In this way, torque can be transmitted to the propeller 50 via the reducer assembly 30, achieving stable propulsion of the propeller 50. It will be appreciated that in this embodiment, torque can be transmitted between the torque input end 31 and the torque output end 32 via a single intermediate transmission shaft 331. In other embodiments, multiple intermediate transmission shafts 331 may be provided to transmit torque, as long as the required torque can be output through the reducer assembly 30.

[0050] It will be appreciated that the transmission ratio between the input gear 313 and the first intermediate gear 333a is greater than 1, meaning that the instantaneous rotation angle of the input gear 313 is much greater than that of the first intermediate gear 333a, and the instantaneous rotation angle of the first intermediate gear 333a is equal to that of the second intermediate gear 333b. The transmission ratio between the second intermediate gear 333b and the output gear 323 is less than 1, meaning that the instantaneous rotation angle of the second intermediate gear 333b is much smaller than that of the output gear 323, thereby effectively meeting the output torque deceleration requirements of the motor 20.

[0051] As shown in Figures 3 and 4, in some embodiments, the cooling lubricant pumped by the pump assembly 40 flows through the intermediate transmission shaft 331. This cooling lubricant can cool or lubricate the intermediate transmission shaft 331, ensuring stable rotation of the intermediate transmission shaft 331. In this embodiment, the cooling lubricant pumped by the pump assembly 40 can flow through part or all of the intermediate transmission shaft 331. For example, the cooling lubricant pumped by the pump assembly 40 can flow through one end of the intermediate transmission shaft 331. It is understood that the pump fluid outlet of the pump assembly 40 can be positioned near one end of the intermediate transmission shaft 331, so that the cooling lubricant pumped by the pump assembly 40 flows through the intermediate transmission shaft 331. The pump fluid outlet of the pump assembly 40 can be positioned near one end of the intermediate transmission shaft 331 via a pipe or a housing flow passage, and this embodiment is not limited thereto. Of course, the pump fluid outlet of the pump assembly 40 can also be positioned near either end of the intermediate transmission shaft 331, or near a location between the two ends of the intermediate transmission shaft 331, and this embodiment is not limited thereto.

[0052] As shown in Figures 3 and 4 , the cooling lubricant pumped by the pump assembly 40 flows through the intermediate shaft bearings 332. It will be appreciated that intermediate shaft bearings 332 are provided at both ends of the intermediate transmission shaft 331, meaning both intermediate shaft bearings 332 can be cooled and lubricated by the cooling lubricant. Alternatively, the cooling lubricant pumped by the pump assembly 40 can be configured to cool and lubricate only one intermediate shaft bearing 332 to increase cooling and lubrication efficiency, while the other intermediate shaft bearing 332 can be cooled and lubricated by the cooling lubricant being rotated and stirred within the second cavity 10b. In this manner, the cooling lubricant can cool or lubricate the intermediate shaft bearings 332, ensuring stable rotation of the intermediate shaft relative to the intermediate shaft bearings 332. In this embodiment, the cooling lubricant pumped by the pump assembly 40 can flow through one or more intermediate shaft bearings 332. For example, the cooling lubricant pumped by the pump assembly 40 can flow through the intermediate shaft bearing 332 at one end of the intermediate shaft.

[0053] In some embodiments, the cooling lubricant pumped by the pump assembly 40 flows through the first intermediate gear 333a and / or the second intermediate gear 333b. In this way, the cooling lubricant can cool or lubricate the first intermediate gear 333a and / or the second intermediate gear 333b to ensure that the intermediate gear 333 can stably transmit torque. In this embodiment, the cooling lubricant pumped by the pump assembly 40 can flow through part or all of the first intermediate gear 333a and / or the second intermediate gear 333b. For example, the cooling lubricant pumped by the pump assembly 40 can flow through the position where the first intermediate gear 333a and / or the second intermediate gear 333b meshes with other gears in the reducer assembly 30, for example, the position where the first intermediate gear 333a and / or the second intermediate gear 333b meshes with other gears in the reducer assembly 30, for example, the position where the first intermediate gear 333a and / or the second intermediate gear 333b meshes with the input gear 313, or the position where the output gear 323 meshes with the output gear 323.

[0054] As shown in FIG2 , in some embodiments, the pump assembly 40 is connected to the input shaft 311 to pump fluid under the torque of the input shaft 311. The input shaft 311 has a high rotational speed and low torque. Therefore, the pump assembly 40 can pump fluid under the action of a relatively high rotational speed and relatively low torque, thereby being able to quickly pump a large amount of cooling and lubricating fluid to the reducer assembly 30, thereby efficiently cooling and lubricating the reducer assembly 30.

[0055] As shown in Figures 1 and 2, in some embodiments, a pump assembly 40 is connected to the output shaft 321 to pump fluid under the torque of the output shaft 321. Since the input shaft 311 has a low rotational speed and high torque, the pump assembly 40 can pump fluid at a relatively low rotational speed and high torque, thereby pumping the cooling and lubricating fluid to the reducer assembly 30 with a relatively high thrust, thereby achieving stable cooling and lubrication effects for the reducer assembly 30. Furthermore, in this embodiment, the pump assembly 40 generates less noise, and its operating life is also extended.

[0056] As shown in Figures 3 and 4, in some embodiments, a pump assembly 40 is connected to an intermediate transmission shaft 331 to pump fluid under the torque of the intermediate transmission shaft 331. The intermediate shaft has a moderate rotational speed and torque. Therefore, the pump assembly 40 can pump fluid at moderate rotational speeds and torques, enabling rapid delivery of large quantities of cooling and lubricating fluid to the reducer assembly 30 under high thrust, thereby achieving stable and efficient cooling and lubrication of the reducer assembly 30. Furthermore, in this embodiment, the pump assembly 40 does not generate excessive noise, ensuring a long operational life.

[0057] As shown in Figures 7 to 9, in some embodiments, the pump assembly 40 includes a pump housing 41, a rotor assembly 401 disposed within the pump housing 41, a liquid inlet path, and a liquid outlet path. The rotor assembly 401 is coupled to the motor shaft 21 and is in communication with the liquid inlet path and the liquid outlet path. The pump housing 41 is provided with a liquid inlet channel 40a and a liquid outlet channel 40b. The liquid inlet channel 40a is configured to form at least a portion of the liquid inlet path, and the liquid outlet channel 40b is configured to form at least a portion of the liquid outlet path. The pump housing 41 is disposed within the housing 10. The rotor assembly 401 can pump the cooling lubricating liquid from the liquid inlet channel 40a to the liquid outlet channel 40b. Under the action of the torque of the motor shaft 21, the rotor assembly 401 can pump the cooling lubricating liquid in the first cavity 10a along the liquid inlet path to the liquid outlet path. The cooling lubricating liquid can flow through the liquid outlet path to the reducer assembly 30 to cool and lubricate the reducer assembly 30. Since the rotor assembly 401 is disposed in the pump housing 41 , when the pump assembly 40 is installed, the pump housing 41 can be directly installed in the second cavity 10 b . This structure is easy to install and compact.

[0058] It is understood that the inlet channel 40a and the outlet channel 40b are structures on the pump housing 41. The inlet channel 40a can form part or all of the inlet path, and the outlet channel 40b can form part or all of the outlet path. For example, the pump assembly 40 can directly pump the cooling lubricating liquid from the bottom of the first cavity 10a through the opening at one end of the inlet channel 40a, or the pump assembly 40 can connect a pipeline to the inlet channel 40a to pump the cooling lubricating liquid from the bottom of the first cavity 10a; the pump assembly 40 can directly pump the cooling lubricating liquid to the reducer assembly 30 through the opening of the outlet channel 40b, or the pump assembly 40 can pump the cooling lubricating liquid to the reducer assembly 30 through a pipeline.

[0059] As shown in Figures 1, 2, 5, and 6, in some embodiments, the pump housing 41 is disposed between the input shaft 311 and the output shaft 321. This allows the pump housing 41 to be close to the input shaft 311 and the output shaft 321, facilitating the pump assembly 40 to pump cooling lubricant to the shafting locations of the input shaft 311 and the output shaft 321. Furthermore, when the cooling lubricant can be pumped to the shafting locations of the input shaft 311 and the output shaft 321, more efficient cooling and lubrication can be achieved.

[0060] As shown in Figures 1, 2, 5, and 6, in some embodiments, a pump housing 41 is disposed between the input shaft 311 and the output shaft 321. The pump housing 41 is provided with a first bearing mounting groove 41a near the torque input end 31, and the input shaft bearing 312 is fixed to the first bearing mounting groove 41a. The first bearing mounting groove 41a formed in the pump housing 41 can be used to mount and fix the input shaft bearing 312 at one end of the input shaft 311. When the pump housing 41 is installed in the second cavity 10b, it can share a housing with the reducer assembly 30 installed in the second cavity 10b. This allows the pump assembly 40 and the reducer assembly 30 to be installed in the second cavity 10b more reasonably and compactly, without taking up additional space. For example, the input shaft bearing 312 at the other end of the input shaft 311 is fixed in the mounting groove formed in the housing 10 to stably support the input shaft 311 and ensure stable rotation of the input shaft 311.

[0061] As shown in Figures 2, 5 and 9, in some embodiments, the pump housing 41 is arranged between the input shaft 311 and the output shaft 321, and the input shaft 311 passes through the pump housing 41 and is connected to the rotor assembly 401. In this way, the aforementioned pump assembly 40 can pump liquid through the torque of the input shaft 311. In addition, the pump assembly 40 can also be reasonably and compactly arranged in the second cavity 10b where the reducer assembly 30 is installed, without taking up additional space. For example, the first rotor shaft 42 of the rotor assembly 401 passes through the through hole of the pump housing 41 and is inserted and fixed in the mounting hole of the input shaft 311 facing the pump housing 41 to achieve coaxial fixed connection.

[0062] As shown in Figures 2, 8, and 9, in some embodiments, the pump housing 41 is provided with a first liquid outlet 40c. The first liquid outlet 40c is connected to the first bearing mounting groove 41a and the liquid outlet channel 40b. Cooling and lubricating liquid can flow through the first liquid outlet 40c to at least one of the end of the input shaft 311 engaged with the first bearing mounting groove 41a and the input shaft bearing 312. The cooling and lubricating liquid pumped to the liquid outlet channel 40b can then flow through the first liquid outlet 40c to the torque input end 31, thereby cooling or lubricating at least one of the end of the input shaft 311 engaged with the first bearing mounting groove 41a and the input shaft bearing 312.

[0063] As shown in Figures 1, 2, 5, and 6, in some embodiments, the pump housing 41 is disposed between the input shaft 311 and the output shaft 321. The pump housing 41 is provided with a second bearing mounting groove 41b proximate to the torque output end 32, and the output shaft bearing 322 is fixed to the second bearing mounting groove 41b. The second bearing mounting groove 41b formed in the pump housing 41 can be used to mount the output shaft bearing 322 at one end of the output end. When the pump housing 41 is installed in the second cavity 10b, it can share a housing with the reducer assembly 30 installed in the second cavity 10b, thereby allowing the pump assembly 40 and the reducer assembly 30 to be installed in the second cavity 10b more reasonably and compactly, without taking up additional space. For example, the output shaft bearing 322 at the other end of the output shaft 321 is fixed in the mounting groove formed in the housing 10 to stably support the output shaft 321 and achieve stable rotation of the output shaft 321.

[0064] As shown in Figures 1, 2, 5 and 6, in some embodiments, the pump housing 41 is arranged between the input shaft 311 and the output shaft 321, and the output shaft 321 passes through the pump housing 41 and is connected to the rotor assembly 401. In this way, the aforementioned pump assembly 40 can pump liquid through the torque of the output shaft 321. In addition, the pump assembly 40 can also be reasonably and compactly arranged in the second cavity 10b where the reducer assembly 30 is installed, without taking up additional space. For example, the first rotor shaft 42 of the rotor assembly 401 passes through the through hole of the pump housing 41 and is inserted and fixed in the mounting hole of the output shaft 321 facing the pump housing 41 to achieve coaxial fixed connection.

[0065] As shown in Figures 2, 7, and 9, in some embodiments, the pump housing 41 is provided with a second liquid outlet 40d. The second liquid outlet 40d is connected to the second bearing mounting groove 41b and the liquid outlet channel 40b. Cooling and lubricating liquid can flow through the second liquid outlet 40d to at least one of the end of the output shaft 321 engaged with the second bearing mounting groove 41b and the output shaft bearing 322. The cooling and lubricating liquid pumped to the liquid outlet channel 40b can flow through the second liquid outlet 40d to the torque output end 32, thereby cooling or lubricating at least one of the end of the output shaft 321 engaged with the second bearing mounting groove 41b and the output shaft bearing 322.

[0066] It is understood that, as shown in Figures 2, 7, and 8, in this embodiment, when the pump housing 41 is disposed between the input shaft 311 and the output shaft 321, a first bearing mounting groove 41a and a second bearing mounting groove 41b can be respectively provided on both sides of the pump housing 41, so that both sides of the pump assembly 40 can share a housing with the reducer assembly 30, thereby enabling the pump assembly 40 and the reducer assembly 30 to be more reasonably and compactly installed in the second cavity 10b without occupying additional space. Of course, as needed, the first bearing mounting groove 41a and the second bearing mounting groove 41b can also be selectively provided on either side of the pump housing 41.

[0067] It can be understood that, as shown in Figures 2, 7 and 8, in this embodiment, when the pump housing 41 is arranged between the input shaft 311 and the output shaft 321, a first bearing mounting groove 41a and a second bearing mounting groove 41b can be respectively provided on both sides of the pump housing 41, and a first liquid outlet hole 40c and a second liquid outlet hole can be respectively provided on both sides of the pump housing 41, so that when the cooling lubricating liquid is pumped to the liquid outlet channel 40b, it can cool or lubricate at least one of the end of the input shaft 311 and the input shaft bearing 312 that cooperate with the first bearing mounting groove 41a, and cool or lubricate at least one of the end of the output shaft 321 and the output shaft bearing 322 that cooperate with the second bearing mounting groove 41b.

[0068] As shown in Figures 2 and 7 to 9, in some embodiments, the pump housing 41 is disposed between the input shaft 311 and the output shaft 321. The pump assembly 40 further includes a liquid guide tube 47 fixed to the pump housing 41. The liquid guide tube 47 is docked with the liquid outlet channel 40b and is provided with a liquid spray port away from the pump housing 41. The liquid spray port is used to spray cooling lubricating liquid to a position of the reducer away from the pump housing 41. It can be understood that the liquid guide tube 47 can be understood as a portion of the liquid outlet path. The cooling lubricating liquid can be pumped to the liquid spray port through the liquid guide tube 47 to spray cooling lubricating liquid to a position of the reducer away from the pump housing 41, thereby achieving cooling and lubrication of the position of the reducer away from the pump housing 41.

[0069] As shown in Figures 2 and 7 to 9 , the liquid conduit 47 can, for example, be combined with the aforementioned first and / or second liquid outlets. This allows the pump assembly 40 to cool and lubricate both the reducer assembly 30 near the pump housing 41 and the reducer assembly 30 farther from the pump housing 41. This allows for comprehensive cooling and lubrication of the reducer assembly 30, ensuring stable operation.

[0070] As shown in Figures 2 and 7-9, in some embodiments, the pump housing 41 is disposed between the input shaft 311 and the output shaft 321. The liquid conduit 47 is provided with a first liquid spray port 471. The first liquid spray port 471 is located near the end of the input shaft 311 away from the pump housing 41 to spray cooling lubricating liquid toward the end of the input shaft 311 and the corresponding input shaft bearing 312. The cooling lubricating liquid can be sprayed from the first liquid spray port 471 along the liquid conduit 47 to cool or lubricate at least one of the end of the input shaft 311 away from the pump housing 41 and the corresponding input shaft bearing 312. Combined with the aforementioned first liquid outlet, comprehensive cooling and lubrication can be achieved for the entire shaft system of the input shaft 311.

[0071] As shown in Figures 2 and 7-9, in some embodiments, the pump housing 41 is disposed between the input shaft 311 and the output shaft 321. The liquid conduit 47 is provided with a second liquid spray port 472. The second liquid spray port 472 is located near the end of the output shaft 321 distal from the input shaft 311 to spray cooling lubricating liquid toward the end of the output shaft 321 and the corresponding output shaft bearing 322. The cooling lubricating liquid can be sprayed from the second liquid spray port 472 along the liquid conduit 47 to cool or lubricate at least one of the end of the output shaft 321 distal from the pump housing 41 and the corresponding output shaft bearing 322. Combined with the aforementioned second liquid outlet, comprehensive cooling and lubrication can be achieved for the entire shaft system of the output shaft 321.

[0072] It is understood that the liquid conduit 47 can be provided with both the first liquid spray port 471 and the second liquid spray port 472 to simultaneously cool and lubricate the shaft system positions of the input shaft 311 and the shaft system positions of the output shaft 321. Of course, as needed, the liquid conduit 47 can alternatively be provided with either the first liquid spray port 471 or the second liquid spray port 472.

[0073] As shown in FIG2 and FIG7 to FIG9 , in some embodiments, the pump housing 41 is disposed between the input shaft 311 and the output shaft 321. The liquid guide tube 47 is provided with a third liquid spray port 473. The third liquid spray port 473 is located between the torque input end 31 and the torque output end 32 to spray cooling lubricating liquid between the torque input end 31 and the torque output end 32. The cooling lubricating liquid can be sprayed from the third liquid spray port 473 along the liquid guide tube 47 to cool or lubricate the portion of the reducer assembly 30 located between the torque input end 31 and the torque output end 32.

[0074] As shown in Figures 3 and 7 , in some other embodiments, the pump housing 41 is disposed between the input shaft 311 and the intermediate transmission shaft 331. This allows the pump housing 41 to be located close to the input shaft 311 and the intermediate transmission shaft 331, facilitating the pump assembly 40 to pump cooling and lubricating liquid to the shafting locations of the input shaft 311 and the intermediate transmission shaft 331. Furthermore, when the cooling and lubricating liquid can be pumped to the shafting locations of the input shaft 311 and the intermediate transmission shaft 331, more efficient cooling and lubrication can be achieved.

[0075] As shown in Figures 3 and 7, in some embodiments, the pump housing 41 is disposed between the input shaft 311 and the intermediate transmission shaft 331. The pump housing 41 defines a third bearing mounting groove 41c proximate the intermediate transmission shaft 331. An intermediate shaft bearing 332 proximate the torque input end 31 is secured within the third bearing mounting groove 41c. The third bearing mounting groove 41c formed in the pump housing 41 allows for the mounting of the intermediate shaft bearing 332 at one end of the intermediate transmission shaft 331. When installed within the second cavity 10b, the pump housing 41 can share a common housing with the reducer assembly 30 installed within the second cavity 10b. This allows for a more compact installation of the pump assembly 40 and the reducer assembly 30 within the second cavity 10b without occupying additional space. For example, the intermediate shaft bearing 332 at the other end of the intermediate transmission shaft 331 is secured within the mounting groove formed in the housing 10, providing stable support for the input shaft 311 and enabling stable rotation of the intermediate shaft bearing 332.

[0076] As shown in Figures 3 and 7, in some embodiments, the pump housing 41 is disposed between the input shaft 311 and the intermediate transmission shaft 331. The pump housing 41 further includes a fifth bearing mounting groove 41d proximal to the input shaft 311, with the input shaft bearing 312 located distal to the output shaft 321 secured to the fifth bearing mounting groove 41d. The fifth bearing mounting groove 41d formed in the pump housing 41 is adapted to secure the input shaft bearing 311 at one end of the input shaft 311. When the pump housing 41 is installed within the second cavity 10b, it can share a common housing with the reducer assembly 30 installed within the second cavity 10b. This allows for a more compact installation of the pump assembly 40 and the reducer assembly 30 within the second cavity 10b without occupying additional space. For example, the input shaft bearing 311 at the other end of the input shaft 311 is secured within the mounting groove formed in the housing 10 to stably support the input shaft 311 and ensure stable rotation of the input shaft 311.

[0077] As shown in Figures 3, 7 and 9, in some embodiments, the pump housing 41 is arranged between the input shaft 311 and the intermediate transmission shaft 331, and the intermediate transmission shaft 331 is inserted into the pump housing 41 at one end close to the input shaft 311 and is connected to the rotor assembly 401. In this way, the aforementioned pump assembly 40 can pump liquid through the torque action of the intermediate transmission shaft 331. In addition, the pump assembly 40 can also be reasonably and compactly arranged in the second cavity 10b where the reducer assembly 30 is installed, without taking up additional space. For example, the first rotor shaft 42 of the rotor assembly 401 passes through the through hole of the pump housing 41 and is inserted and fixed in the mounting hole of the intermediate transmission shaft 331 facing the pump housing 41 to achieve coaxial fixed connection.

[0078] As shown in Figures 3, 7, and 9, in some embodiments, the pump housing 41 is disposed between the input shaft 311 and the intermediate transmission shaft 331. The pump housing 41 is provided with a third liquid outlet, which is connected to the third bearing mounting groove 41c and the liquid outlet channel 40b. Cooling and lubricating liquid can flow through the third liquid outlet to at least one of the end of the intermediate transmission shaft 331 engaged with the third bearing mounting groove 41c and the intermediate shaft bearing 332. The cooling and lubricating liquid pumped into the liquid outlet channel 40b can flow through the third liquid outlet to the shaft system of the intermediate transmission shaft 331, thereby cooling or lubricating at least one of the end of the intermediate transmission shaft 331 engaged with the third bearing mounting groove 41c and the intermediate shaft bearing 332.

[0079] As shown in Figures 3, 7, and 9, in some embodiments, the pump housing 41 is disposed between the input shaft 311 and the intermediate transmission shaft 331. The pump assembly 40 further includes a liquid guide tube 47 fixed to the pump housing 41. The liquid guide tube 47 is connected to the liquid outlet channel 40b and is capable of spraying cooling lubricating liquid through a liquid spray port to the end of the intermediate transmission shaft 331 away from the pump housing 41. Combined with the third liquid outlet hole, the shaft system position of the intermediate transmission shaft 331 can be fully cooled and lubricated. In addition, when the shaft system position of the intermediate transmission shaft 331 is located above the torque input end 31 and the torque output end 32, the cooling lubricating liquid flowing to both ends of the intermediate transmission shaft 331 can also flow to the torque input end 31 and the torque output end 32 at the same time, thereby achieving comprehensive cooling and lubrication of the reducer assembly 30 to ensure stable operation of the reducer assembly 30.

[0080] As shown in Figures 4 and 7 , in yet other embodiments, the pump housing 41 is disposed between the output shaft 321 and the intermediate transmission shaft 331. This allows the pump housing 41 to be positioned close to the output shaft 321 and the intermediate transmission shaft 331, facilitating the pump assembly 40 to pump cooling and lubricating liquid to the shafting locations of the output shaft 321 and the intermediate transmission shaft 331. Furthermore, when the cooling and lubricating liquid can be pumped to the shafting locations of the output shaft 321 and the intermediate transmission shaft 331, more efficient cooling and lubrication can be achieved.

[0081] As shown in Figures 4 and 7, in some embodiments, the pump housing 41 is disposed between the output shaft 321 and the intermediate transmission shaft 331. The pump housing 41 defines a fourth bearing mounting groove 41e near the intermediate transmission shaft 331. The intermediate shaft bearing 332 near the torque output end 32 is secured within the fourth bearing mounting groove 41e. The fourth bearing mounting groove 41e formed in the pump housing 41 allows for the intermediate shaft bearing 332 at one end of the intermediate transmission shaft 331 to be mounted and secured. When installed within the second cavity 10b, the pump housing 41 can share a common housing with the reducer assembly 30 installed within the second cavity 10b. This allows for a more compact installation of the pump assembly 40 and the reducer assembly 30 within the second cavity 10b without occupying additional space. For example, the intermediate shaft bearing 332 at the other end of the intermediate transmission shaft 331 is secured within a mounting groove formed in the housing 10 to stably support the input shaft 311 and ensure stable rotation of the intermediate shaft bearing 332.

[0082] As shown in Figures 4 and 7, in some embodiments, the pump housing 41 is disposed between the output shaft 321 and the intermediate transmission shaft 331. The pump housing 41 further includes a sixth bearing mounting groove 41f proximal to the output shaft 321, and the output shaft bearing 322 on the side away from the input shaft 311 is fixed to the sixth bearing mounting groove 41f. The sixth bearing mounting groove 41f formed in the pump housing 41 can be mounted to fix the output shaft 321 bearing at one end of the output shaft 321. When the pump housing 41 is installed in the second cavity 10b, it can share a housing with the reducer assembly 30 installed in the second cavity 10b, thereby allowing the pump assembly 40 and the reducer assembly 30 to be installed in the second cavity 10b more reasonably and compactly, without taking up additional space. For example, the output shaft 321 bearing at the other end of the output shaft 321 is fixed in the mounting groove formed in the housing 10 to stably support the output shaft 321 and achieve stable rotation of the output shaft 321.

[0083] As shown in Figures 4, 7 and 9, in some embodiments, the pump housing 41 is arranged between the output shaft 321 and the intermediate transmission shaft 331, and the intermediate transmission shaft 331 is inserted into the pump housing 41 at one end close to the output shaft 321 and is connected to the rotor assembly 401. In this way, the aforementioned pump assembly 40 can pump liquid through the torque action of the intermediate transmission shaft 331. In addition, the pump assembly 40 can also be reasonably and compactly arranged in the second cavity 10b where the reducer assembly 30 is installed, without taking up additional space. For example, the first rotor shaft 42 of the rotor assembly 401 passes through the through hole of the pump housing 41 and is inserted and fixed in the mounting hole of the intermediate transmission shaft 331 facing the pump housing 41 to achieve coaxial fixed connection.

[0084] As shown in Figures 4, 7, and 9, in some embodiments, the pump housing 41 is disposed between the output shaft 321 and the intermediate transmission shaft 331. The pump housing 41 is provided with a fourth liquid outlet, which is connected to the third bearing mounting groove 41c and the liquid outlet channel 40b. Cooling and lubricating liquid can flow through the fourth liquid outlet to at least one of the end of the intermediate transmission shaft 331 engaged with the third bearing mounting groove 41c and the intermediate shaft bearing 332. The cooling and lubricating liquid pumped into the liquid outlet channel 40b can flow through the fourth liquid outlet to the shaft system of the intermediate transmission shaft 331, thereby cooling or lubricating at least one of the end of the intermediate transmission shaft 331 engaged with the third bearing mounting groove 41c and the intermediate shaft bearing 332.

[0085] As shown in Figures 4, 7 and 9, in some embodiments, the pump housing 41 is disposed between the output shaft 321 and the intermediate transmission shaft 331. The pump assembly 40 further includes a liquid guide tube 47 fixed to the pump housing 41. The liquid guide tube 47 is docked with the liquid outlet channel 40b and is capable of spraying cooling lubricating liquid through a liquid spray port to the end of the intermediate transmission shaft 331 away from the pump housing 41. Combined with the fourth liquid outlet hole, the shaft position of the intermediate transmission shaft 331 can be fully cooled and lubricated. In addition, when the shaft position of the intermediate transmission shaft 331 is located above the torque input end 31 and the torque output end 32, the cooling lubricating liquid flowing to both ends of the intermediate transmission shaft 331 can also flow to the torque input end 31 and the torque output end 32 at the same time, thereby achieving comprehensive cooling and lubrication of the reducer assembly 30 to ensure stable operation of the reducer assembly 30.

[0086] As shown in Figures 1 to 4, in some embodiments, the pump assembly 40 can pump liquid under the forward torque or reverse torque of the motor shaft 21. It is understandable that when the motor shaft 21 rotates forward or reverse, it will drive the propeller 50 to rotate in different directions. Regardless of whether the motor shaft 21 rotates forward or reverse, liquid can be pumped. In other words, as long as the motor 20 is running, liquid can be pumped. The electric propeller 100 can ensure that the pump assembly 40 stably pumps liquid in any operating state, thereby achieving cooling and lubrication of the reducer under any circumstances.

[0087] As shown in Figures 1 and 7 to 9, in some embodiments, a rotor assembly 401 includes a first rotor shaft 42, a first rotor 43, and a second rotor 44. The first rotor shaft 42 is coupled to the motor shaft 21, and the first rotor 43 is concentrically connected to the first rotor shaft 42. The second rotor 44 has an eccentric hole therein. The first rotor 43 eccentrically engages with the eccentric hole, and cooling and lubricating fluid is pumped from the inlet channel 40a through the gap between the eccentric hole and the first rotor 43 to the outlet channel 40b. When the motor 20 is running, the torque of the motor shaft 21 drives the first rotor shaft 42 to rotate, thereby driving the first rotor 43 to rotate. Due to the eccentric engagement of the first rotor 43 with the eccentric hole, as the first rotor 43 rotates eccentrically relative to the eccentric hole, cooling and lubricating fluid is continuously pumped from the gap between the eccentric hole and the first rotor 43 through the inlet channel 40a to the outlet channel 40b, thereby completing the pumping process. This structure is simple and highly efficient.

[0088] As shown in Figures 7-9, rotor assembly 401 also includes a rotor retaining ring 45, which is mounted around the outer periphery of second rotor 44 to define the offset position of second rotor 44 relative to first rotor 43. With the offset position of second rotor 44 defined, first rotor 43 can stably rotate eccentrically with the eccentric hole at a specific position to complete liquid pumping. It will be appreciated that the offset position of second rotor 44 ensures that the eccentric hole is connected to both the inlet channel 40a and the outlet channel 40b, thereby ensuring stable liquid pumping by first rotor 43.

[0089] As shown in Figures 1 and 7 to 9, in some embodiments, the liquid outlet path is provided with at least one forward liquid outlet channel 40b and at least one reverse liquid outlet channel 40b, and both the forward liquid outlet channel 40b and the reverse liquid outlet channel 40b are connected to the rotor assembly 401. When the motor 20 rotates forward, the liquid outlet rate of the forward liquid outlet channel 40b is greater than the liquid outlet rate of the reverse liquid outlet channel 40b, and when the motor 20 rotates reversely, the liquid outlet rate of the reverse liquid outlet channel 40b is greater than the liquid outlet rate of the forward liquid outlet channel 40b. When the motor 20 rotates forward, the forward liquid outlet channel 40b can stably discharge liquid, and when the motor 20 rotates reversely, the reverse liquid outlet channel 40b can stably discharge liquid, so as to ensure that the motor 20 can stably pump liquid in both forward and reverse rotations. For example, when the motor 20 rotates forward, the rotor limit ring 45 can bias the second rotor 44 so that the liquid discharge rate of the forward liquid outlet channel 40b is greater than the liquid discharge rate of the reverse liquid outlet channel 40b; when the motor 20 rotates reversely, the rotor limit ring 45 can bias the second rotor 44 so that the liquid discharge rate of the reverse liquid outlet channel 40b is greater than the liquid discharge rate of the forward liquid outlet channel 40b.

[0090] As shown in Figures 7 to 9, the pump assembly 40 is illustratively provided with a blocking member 46. The rotor limiting ring 45 is coaxially rotated with the second rotor 44. The blocking member 46 is used to locate the rotational position of the rotor limiting ring 45, thereby positioning the second rotor 44 in an offset direction relative to the first rotor 43. It is understood that when the first rotor 43 rotates, the first rotor 43 will contact the second rotor 44 and drive the second rotor 44 to rotate in the same direction. Since the rotor limiting ring 45 is coaxially rotated with the second rotor 44, it will also drive the rotor limiting ring 45 to rotate. After the rotor limiting ring 45 rotates, the blocking member 46 locates the rotational position of the rotor limiting ring 45, thereby positioning the offset direction of the second rotor 44.

[0091] For example, as shown in Figures 1 and 7 to 9, when the motor 20 rotates forward, the rotor retaining ring 45 rotates to the first position and contacts the blocking member 46, causing the gap between the second rotor 44 and the first rotor 43 to be offset and connected to the forward liquid outlet channel 40b. When the motor 20 rotates reversely, the rotor retaining ring 45 rotates to the second position and contacts the blocking member 46, causing the gap between the second rotor 44 and the first rotor 43 to be offset and connected to the reverse liquid outlet channel 40b. In this way, when the motor 20 rotates forward and reverse, the rotor retaining ring 45 can be positioned at different positions by the blocking member 46, thereby offsetting the second rotor 44 to different positions, and the first rotor 43 can complete the pumping of liquid at different positions when the motor 20 rotates forward and reverse.

[0092] As shown in Figures 1 and 7 to 9, the rotor limiting ring 45 is exemplarily provided with a mating boss 451. One side of the mating boss 451 forms a first blocking portion, and the other side of the mating boss 451 forms a second blocking portion. When the motor 20 rotates forward, the rotor limiting ring 45 rotates forward, and the first blocking portion abuts against the blocking member 46. When the motor 20 rotates reversely, the rotor limiting ring 45 reverses, and the second blocking portion abuts against the blocking member 46. When the motor 20 rotates forward, the rotor limiting ring 45 rotates to the first position, and the first blocking portion abuts against the blocking member 46 to position the rotor limiting ring 45. When the motor 20 rotates reversely, the rotor limiting ring 45 rotates to the second position, and the second blocking portion abuts against the blocking member 46 to position the rotor limiting ring 45.

[0093] In other embodiments, a single outlet channel 40b is provided. When the motor 20 rotates forward or reverse, the cooling and lubricating liquid in the inlet channel 40a is pumped to the outlet channel 40b. This structure is simple and can ensure stable liquid discharge. For example, the position of the rotor retaining ring 45 can be fixed to ensure stable liquid pumping regardless of whether the first rotor 43 rotates forward or reverse.

[0094] As shown in Figures 7 to 9, in some embodiments, the pump housing 41 includes a second housing 412 and a first housing 411 connected to each other, the rotor assembly 401 is disposed within the second housing 412, and the liquid inlet channel 40a and the liquid outlet channel 40b are disposed between the first housing 411 and the second housing 412. In this way, the pump assembly 40 is installed.

[0095] Exemplarily, the blocking member 46 is provided on the first housing 411 to limit the rotor limiting ring 45 .

[0096] Exemplarily, the first rotor shaft 42 passes through the through hole of the second housing 412 and is inserted and fixed in the mounting hole of the output shaft 321 facing the pump housing 41 .

[0097] Exemplarily, as shown in Figures 6 to 9, the second shell 412 is provided with a second bearing mounting groove 41b and a second liquid outlet 40d, and the other side of the second shell 412 and the first shell 411 are surrounded by a first bearing mounting groove 41a, and the first shell 411 is provided with a first liquid outlet 40c, so that when the cooling lubricating liquid is pumped to the liquid outlet channel 40b, it can cool or lubricate at least one of the end of the input shaft 311 and the input shaft bearing 312 that cooperate with the first bearing mounting groove 41a, and cool or lubricate at least one of the end of the output shaft 321 and the output shaft bearing 322 that cooperate with the second bearing mounting groove 41b.

[0098] As shown in Figures 1 and 6, in some embodiments, the pump housing 41 is fixedly connected to the housing 10. In this way, the pump assembly 40 is fixed in the second cavity 10b to ensure stable pumping of liquid.

[0099] As shown in Figures 7 to 9, some embodiments further include a filter 48, which is disposed in the fluid inlet path to filter the cooling and lubricating fluid entering the fluid inlet path. Filter 48 can filter the cooling and lubricating fluid drawn by the power pump system to prevent impurities from entering the pump circuit and affecting the cooling and lubrication of the reducer assembly 30.

[0100] For example, filter 48 is equipped with a magnetic element 481 for absorbing magnetically attractable impurities in the cooling lubricant. This further prevents magnetically attractable impurities from entering the circulation. For example, the magnetic element is positioned adjacent to the outer wall of filter 48 to attract magnetically attractable impurities in the cooling lubricant as it enters the filter 48.

[0101] Exemplarily, the filter 48 is an oil suction filter, which can prevent the suction of pollutants and impurities, thereby ensuring the cleanliness of the power pump system and the stable circulation of the cooling lubricant.

[0102] Exemplarily, filter 48 is a pressure filter. Depending on the filter medium used, the pressure filter can achieve different filtering effects. For example, when filled with activated carbon, it can adsorb pigments, organic matter, residual chlorine, colloids, etc. in the cooling and lubricating fluid to ensure stable circulation of the cooling and lubricating fluid.

[0103] As shown in Figures 7 to 9, in some embodiments, a filter 48 is removably disposed within the liquid inlet passage. This allows for removal as needed to facilitate replacement or cleaning of the filter 48, effectively filtering the circulating cooling lubricant. Exemplarily, the filter 48 is a plate-type filter 48 that can be screwed to the liquid inlet of the liquid inlet passage 40a for installation. The magnetic element 481 can also be screwed to the filter 48.

[0104] In other embodiments, filter 48 is non-removably disposed within the fluid inlet path. This ensures stable pumping by the power pump system, and ensures that all cooling and lubricating fluid entering the fluid inlet path passes through filter 48, effectively filtering the cooling and lubricating fluid. For example, a portion of the fluid inlet path may be detachably connected to pump assembly 40, allowing for direct removal of the portion of the fluid inlet path for easy replacement or cleaning of filter 48.

[0105] As shown in Figures 1 to 4 and 10, an embodiment of the present application further provides a movable water area device 1000, comprising a water area carrier 200 and the aforementioned electric propeller 100, wherein the electric propeller 100 is connected to the water area carrier 200. The electric propeller 100 can be connected to the water area carrier 200 via a housing 10, or via a clamp connected to the housing 10, or via a support assembly connected to the housing, so as to achieve installation of the electric propeller 100 on the water area carrier 200.

[0106] In the water area movable device 1000 provided in the embodiment of the present application, the electric propeller 100 can propel the water area carrier 200 to move, so as to enable the water area movable device 1000 to move on the water area. In the electric propeller 100, the cooling lubricating liquid located in the first cavity 10a can be heat-exchanged with the water outside the shell 10 through the shell 10, so that the cooling lubricating liquid is cooled. Since the pump assembly 40 is located in the second cavity 10b, the pump assembly 40 can complete the pumping of liquid under the torque of the motor shaft 21, and pump the cooling lubricating liquid into contact with the reducer assembly 30 to achieve cooling and lubrication of the reducer assembly 30. Without the need for additional power structure and space, stable cooling and lubrication of the reducer assembly 30 can be achieved. The water area movable device 1000 provided in the present application can achieve cooling and lubrication effects on the reducer assembly 30, increase the service life of the reducer assembly 30, and reduce the failure rate of the electric propeller 100.

[0107] The above description is only a preferred embodiment of the present application and does not limit the patent scope of the present application. All equivalent structural transformations made based on the contents of the present application specification and drawings, or direct / indirect application in other related technical fields, are included in the patent protection scope of the present application.

Claims

1. An electric propeller, wherein: include: A shell, comprising a first cavity and a second cavity isolated from the first cavity, wherein the second cavity is used to contain a cooling lubricating liquid, and the cooling lubricating liquid can exchange heat with water outside the shell through the shell; A motor is disposed in the first cavity, and the motor is provided with a motor shaft; A reducer assembly, disposed in the second cavity and coupled to the motor shaft; A pump assembly is disposed in the second cavity, the pump assembly is coupled to the motor shaft to pump liquid under the torque of the motor shaft, the cooling lubricating liquid can be pumped away from the bottom of the second cavity under the pumping of the pump assembly, and return to the bottom of the second cavity after contacting at least part of the reducer assembly; A propeller is located outside the housing and is connected to the reducer assembly shaft.

2. The electric thruster according to claim 1, wherein: The reducer assembly is provided with a torque input end and a torque output end, wherein the torque input end receives the torque of the motor, and the torque output end outputs the torque to the propeller, and the pump assembly is arranged at the torque input end or the torque output end, or at a portion between the torque input end and the torque output end.

3. The electric thruster according to claim 2, wherein: The torque input end is provided with an input shaft capable of receiving the motor torque, an input shaft bearing matched with the input shaft and fixed in the housing, and an input gear fixed to the input shaft; the torque output end is provided with an output shaft capable of outputting torque to the propeller, an output shaft bearing matched with the output shaft and fixed in the housing, and an output gear fixed to the output shaft, and the output gear receives the rotational torque from the input gear.

4. The electric propulsion device according to claim 3, wherein: The cooling lubricating fluid pumped out by the pump assembly flows through the input shaft.

5. The electric propulsion device according to claim 3, wherein: The cooling lubricating fluid pumped out by the pump assembly flows through the input shaft bearing.

6. The electric thruster according to claim 3, wherein: The cooling lubricating fluid pumped out by the pump assembly flows through the input gear.

7. The electric thruster according to claim 3, wherein: The cooling lubricating fluid pumped out by the pump assembly flows through the output shaft.

8. The electric thruster according to claim 3, wherein: The cooling lubricating fluid pumped out by the pump assembly flows through the output shaft bearing.

9. The electric thruster according to claim 3, wherein: The cooling lubricating fluid pumped out by the pump assembly flows through the output gear.

10. The electric thruster according to claim 3, wherein: The reducer assembly is also provided with an intermediate transmission shaft connected between the torque input end and the torque output end, an intermediate shaft bearing cooperating with the intermediate transmission shaft and fixed in the housing, and a first intermediate gear and a second intermediate gear fixed to the intermediate transmission shaft, the first intermediate gear meshing with the input gear, and the second intermediate gear meshing with the output gear.

11. The electric thruster according to claim 10, wherein: The cooling lubricating fluid pumped out by the pump assembly flows through the intermediate transmission shaft.

12. The electric thruster according to claim 10, wherein: The cooling lubricating fluid pumped out by the pump assembly flows through the intermediate shaft bearing.

13. The electric thruster according to claim 10, wherein: The cooling lubricating fluid pumped out by the pump assembly flows through the first intermediate gear and / or the second intermediate gear.

14. The electric thruster according to claim 3, wherein: The pump assembly is connected to the input shaft to pump fluid under the torque of the input shaft.

15. The electric thruster according to claim 3, wherein: The pump assembly is connected to the output shaft to pump fluid under the torque of the output shaft.

16. The electric thruster according to claim 10, wherein: The pump assembly is connected to the intermediate transmission shaft to pump fluid under the torque of the intermediate transmission shaft.

17. The electric thruster according to claim 10, wherein: The pump assembly includes a pump housing, a rotor assembly arranged in the pump housing, a liquid inlet path and a liquid outlet path, the rotor assembly is coupled to the motor shaft, the rotor assembly is connected to the liquid inlet path and the liquid outlet path, the pump housing is provided with a liquid inlet channel and a liquid outlet channel, the liquid inlet channel is at least configured to form a portion of the liquid inlet path, the liquid outlet channel is at least configured to form a portion of the liquid outlet path, the pump housing is arranged in the casing, and the rotor assembly can pump the cooling lubricating liquid in the liquid inlet channel to the liquid outlet channel.

18. The electric thruster according to claim 17, wherein: The pump housing is disposed between the input shaft and the output shaft.

19. The electric thruster according to claim 18, wherein: The pump housing is provided with a first bearing mounting groove close to the torque input end, and the input shaft bearing is fixed in the first bearing mounting groove.

20. The electric thruster according to claim 19, wherein: The input shaft passes through the pump housing and is connected to the rotor assembly.

21. The electric thruster according to claim 19, wherein: The pump housing is provided with a first liquid outlet hole, which is connected to the first bearing mounting groove and the liquid outlet channel, and the cooling lubricating liquid can flow along the first liquid outlet hole to at least one of the end of the input shaft matched with the first bearing mounting groove and the input shaft bearing.

22. The electric thruster of claim 18, wherein: The pump housing is provided with a second bearing mounting groove close to the torque output end, and the output shaft bearing is fixed in the second bearing mounting groove.

23. The electric thruster according to claim 22, wherein: The output shaft passes through the pump housing and is connected to the rotor assembly.

24. The electric thruster of claim 22, wherein: The pump housing is provided with a second liquid outlet hole, which is connected to the second bearing mounting groove and the liquid outlet channel, and the cooling lubricating liquid can flow along the second liquid outlet hole to at least one of the end of the output shaft and the output shaft bearing that cooperates with the second bearing mounting groove.

25. The electric thruster of claim 18, wherein: The pump assembly also includes a liquid guide tube fixed to the pump housing, the liquid guide tube is connected to the liquid outlet channel, and is provided with a liquid spray port away from the pump housing, and the liquid spray port is used to spray the cooling lubricating liquid to a position of the reducer assembly away from the pump housing.

26. The electric thruster according to claim 25, wherein: The liquid guide pipe is provided with a first liquid spray port, which is close to the end of the input shaft away from the pump housing, so as to spray the cooling lubricating liquid to the end of the input shaft and the corresponding matching input shaft bearing.

27. The electric thruster of claim 25, wherein: The liquid guide pipe is provided with a second liquid spray port, and the second liquid spray port is close to the end of the output shaft away from the pump housing, so as to spray the cooling lubricating liquid to the end of the output shaft and the corresponding output shaft bearing.

28. The electric thruster of claim 17, wherein: The pump housing is arranged between the input shaft and the intermediate transmission shaft.

29. The electric thruster of claim 28, wherein: The pump housing is provided with a third bearing installation groove close to the intermediate transmission shaft, and the intermediate shaft bearing close to the torque input end is fixed in the third bearing installation groove.

30. The electric thruster of claim 29, wherein: One end of the intermediate transmission shaft close to the input shaft penetrates into the pump housing and is connected to the rotor assembly.

31. The electric thruster of claim 17, wherein: The pump housing is arranged between the output shaft and the intermediate transmission shaft.

32. The electric thruster of claim 31, wherein: The pump housing is provided with a fourth bearing mounting groove close to the intermediate transmission shaft, and the intermediate shaft bearing close to the torque output end is fixed in the fourth bearing mounting groove.

33. The electric thruster of claim 32, wherein: One end of the intermediate transmission shaft close to the output shaft penetrates into the pump housing and is connected to the rotor assembly.

34. The electric thruster of claim 1, wherein: The pump assembly can pump liquid under either the forward torque or the reverse torque of the motor shaft.

35. The electric thruster of claim 17, wherein: The rotor assembly includes a first rotor shaft, a first rotor and a second rotor. The first rotor shaft is coupled to the motor shaft. The first rotor is concentrically connected to the first rotor shaft. An eccentric hole is provided in the second rotor. The first rotor is eccentrically matched with the eccentric hole. The cooling lubricating liquid is pumped from the liquid inlet channel to the liquid outlet channel through the gap between the eccentric hole and the first rotor.

36. An electric thruster as claimed in claim 35, wherein: The rotor assembly further includes a rotor limiting ring, which is sleeved on the outer circumference of the second rotor to limit the offset position of the second rotor relative to the first rotor.

37. An electric thruster as claimed in claim 36, wherein: The liquid outlet path is provided with at least one forward liquid outlet channel and at least one reverse liquid outlet channel, and both the forward liquid outlet channel and the reverse liquid outlet channel are connected to the rotor assembly. When the motor rotates forward, the liquid outlet rate of the forward liquid outlet channel is greater than the liquid outlet rate of the reverse liquid outlet channel. When the motor rotates reversely, the liquid outlet rate of the reverse liquid outlet channel is greater than the liquid outlet rate of the forward liquid outlet channel.

38. The electric thruster of claim 37, wherein: The pump assembly is provided with a blocking member, the rotor limiting ring is coaxially rotated with the second rotor, and the blocking member is used to locate the rotational position of the rotor limiting ring to locate the offset direction of the second rotor relative to the first rotor.

39. The electric thruster of claim 38, wherein: When the motor rotates forward, the rotor limit ring rotates to the first position and conflicts with the blocking member, and the gap offset between the second rotor and the first rotor is connected to the forward liquid outlet channel; when the motor rotates reversely, the rotor limit ring rotates to the second position and conflicts with the blocking member, and the gap offset between the second rotor and the first rotor is connected to the reverse liquid outlet channel.

40. The electric thruster of claim 39, wherein: The rotor limiting ring is provided with a matching boss, one side of the matching boss forms a first blocking portion, and the other side of the matching boss forms a second blocking portion. When the motor rotates forward, the rotor limiting ring rotates forward, and the first blocking portion abuts against the blocking member; when the motor rotates reversely, the rotor limiting ring reverses, and the second blocking portion abuts against the blocking member.

41. The electric thruster of claim 17, wherein: It also includes a filter, which is arranged in the liquid inlet path to filter the cooling lubricating liquid entering the liquid inlet path.

42. An electric thruster as claimed in claim 41, wherein: The filter is provided with a magnetic attraction member for absorbing magnetically attractable impurities of the cooling lubricating fluid.

43. A movable device in water area, wherein: It comprises a water area carrier and an electric propeller as described in any one of claims 1 to 42, wherein the electric propeller is connected to the water area carrier.

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