Variable flow cooling structure of motor rotor

Abstract

The utility model relates to a variable flow cooling structure of a motor rotor, which comprises a rotating shaft and a rotor core, two ends of the rotor core are respectively provided with a rotor baffle A and a rotor baffle B, the rotor core is provided with a plurality of rotor core axial oil ways, the rotor baffle A and the rotor baffle B are provided with a plurality of radial oil ways communicated with the rotor core axial oil ways, and the radial oil ways are communicated with the rotor core axial oil ways. A middle axial oil hole is formed in the rotating shaft, a side wall oil hole is further formed in the side wall of the rotating shaft, the rotating shaft is communicated with the reduction gearbox shaft valve seat, the rotor assembly is further provided with an oil quantity distribution mechanism, the oil quantity distribution mechanism comprises a valve rod which is arranged in the rotating shaft and extends in the axial direction, and the reduction gearbox shaft valve seat is in a hollow tube shape and is provided with a protruding ring on the inner wall. A gap is formed between one end of the valve rod and the inner wall of the convex ring, the gap is enlarged by changing the position of the valve rod, and then the oil inlet amount of the middle axial oil hole is increased. According to the utility model, the requirements of the rotor assembly and the stator assembly on the cooling oil quantity under different working conditions are met, and real-time oil quantity distribution of the stator and the rotor is realized.

Description

Technical Field

[0001] The utility model relates to a drive motor for a vehicle, and more specifically, to a variable flow cooling structure for a motor rotor. Background Art

[0002] An electric motor is an electromagnetic device that realizes the conversion or transmission of electrical energy based on the law of electromagnetic induction. Its main function is to generate a driving torque. As an electrical appliance or the power source of various machines, when the motor runs at high speed, components such as coils and rotor cores will generate a large amount of heat. Therefore, water cooling or oil cooling methods are often used to dissipate heat from the motor.

[0003] The existing oil-cooled motor uses two flow paths to cool the motor. Specifically, before the main flow path enters the transmission, a part of the coolant branches to the motor housing, and the stator end is cooled through the liquid holes on the motor housing; another part of the coolant enters the transmission. After the transmission oil comes out of the transmission shaft, it passes through the flow path on the rotor support. Through the rotation of the rotor, the transportation of the oil is driven, so that the oil is completely transported to the stator end to achieve the purpose of cooling the motor.

[0004] The existing oil-cooled cooling and lubrication structure cannot ensure sufficient cooling of each component in the electric drive system assembly. Moreover, after the conventional powertrain structure is designed, the ratio of the amount of lubricating oil distributed to the stator assembly and the rotor assembly is fixed. However, under the same working conditions, the stator assembly and the rotor assembly generate different amounts of heat, and the required cooling oil amounts are also inconsistent. The conventional lubrication and cooling structure cannot meet the requirements of different cooling oil flows for the stator and rotor, and cannot maximize the cooling efficiency.

[0005] Although there is also a technology for adjusting the stator and rotor flow rates in the prior art. For example, Chinese invention patent CN115139771B discloses an electric motor system and a vehicle having the electric motor system. The electric motor system includes: an electric motor, the electric motor includes: a motor housing, a stator core, a stator winding, a rotor core. The stator core is installed in the motor housing, the stator winding is wound around the stator core, the rotor core is rotatably arranged relative to the stator core, a rotor flow path is at least formed in the rotor core, and the rotor flow path is adapted to convey a coolant to the stator winding; a valve for controlling the flow rate of the rotor flow path. According to the electric motor system of the present utility model, the flow rate of the rotor flow path can be adjusted by opening and closing the valve. Thus, when the rotor flow path is needed to cool the motor, the valve is opened to ensure that the flow rate in the rotor flow path is not zero; when the rotor flow path is not needed to cool the motor, the valve is closed to ensure that the flow rate in the rotor flow path is adjusted to zero, thereby reducing the energy consumption during the rotation of the rotor and optimizing the efficiency of the motor. However, the above structure requires a series of sensors to be arranged in the motor, the overall structure is complex, and the control effect is not good. Summary of the Utility Model

[0006] In order to solve the above technical problems, the purpose of the present utility model is to provide a variable-flow cooling structure for a motor rotor, which can meet the distribution of the cooling oil volume of the stator and rotor under different working conditions.

[0007] In order to achieve the above utility model purpose, the present utility model adopts the following technical solutions:

[0008] A variable-flow cooling structure for a motor rotor includes a rotating shaft and a rotor core fixedly sleeved on the rotating shaft. Rotor baffles A and B are respectively provided at both ends of the rotor core. A plurality of axial oil channels of the rotor core are provided on the rotor core. A plurality of radial oil channels communicating with the axial oil channels of the rotor core are provided on the rotor baffles A and B. The interior of the rotating shaft is hollow to form a central axial oil hole. Side wall oil holes for communicating the central axial oil hole with some of the radial oil channels are also provided on the side wall of the rotating shaft. The rotating shaft is connected with a reduction gearbox shaft valve seat and is communicated with the reduction gearbox shaft valve seat. An oil volume distribution mechanism is further provided on the rotor assembly. The oil volume distribution mechanism includes a valve rod arranged in the rotating shaft and extending axially. The reduction gearbox shaft valve seat is a hollow tube, and an inner wall is provided with a convex ring. There is a gap between one end of the valve rod and the inner wall of the convex ring. By changing the position of the valve rod, the gap becomes larger, and thus the oil inflow volume of the central axial oil hole increases.

[0009] As a preferred scheme: There are a plurality of the convex rings, and the inner diameters increase sequentially along the moving direction of the valve rod.

[0010] As a preferred scheme: The oil volume distribution mechanism further includes an installation chassis and a worm. A valve core is provided at one end of the valve rod, and the other end of the valve rod is a rack section. The installation chassis is sleeved and fixed on the rotating shaft. Support blocks are provided on both sides of the rotating shaft on the installation chassis. The worm penetrates through the support blocks and the rotating shaft, and the worm meshes with the rack section of the valve rod for transmission. A counterweight ball is provided at one end of the worm, and a reset assembly is provided at the other end. When the rotor assembly rotates, the counterweight ball drives the worm to move radially under the action of centrifugal force, and thus the valve rod meshing with the worm moves axially, so that the valve core moves away from the convex ring, and thus the oil inflow volume of the central axial oil hole increases.

[0011] As a preferred scheme: There are two worms, which are respectively located on both sides of the rack section and both mesh with the rack section for transmission. The counterweight balls of the two worms are respectively located on both sides of the rotating shaft.

[0012] As a preferred scheme: A limiting groove is further provided on the inner wall of the rotating shaft. Convex blocks are respectively provided at both ends of the rack section on the valve rod. The convex blocks are arranged in the limiting groove and slide in the limiting groove along with the movement of the valve rod.

[0013] As a preferred solution: spray holes B are provided on both the rotor baffle A and the rotor baffle B. The radial oil passage includes a baffle radial oil passage A and a baffle radial oil passage B. One end of the baffle radial oil passage A is communicated with the axial oil passage of the rotor core, and the other end is communicated with the spray hole B. One end of the baffle radial oil passage B is communicated with the axial oil passage of the rotor core, and the other end is communicated with the side wall oil hole.

[0014] As a preferred solution: the baffle radial oil passage A and the baffle radial oil passage B are arranged at equal intervals circumferentially, and the positions of the baffle radial oil passage A on the rotor baffle A and the rotor baffle B are staggered with each other.

[0015] As a preferred solution: the spray hole B is close to the outer edge of the rotor baffle A or the rotor baffle B, and the spray hole B is inclined from the inside to the outside.

[0016] As a preferred solution: a bearing is further provided on the rotating shaft, and a bearing lubricating oil hole is provided on one side of the rotating shaft where the bearing is located. The bearing lubricating oil hole is communicated with the middle axial oil hole.

[0017] As a preferred solution: a shaft shoulder is provided at one end of the rotating shaft. The rotor baffle B abuts against the shaft shoulder. One side of the rotor baffle A abuts against the rotor core, and the other side is axially limited by a steel pressing ring that is in interference fit with the rotating shaft.

[0018] Compared with the prior art, the beneficial effects of the present utility model are as follows:

[0019] By providing oil passages on the rotating shaft and the rotor core, and further providing an oil quantity distribution mechanism on the rotor assembly, by changing the distance between the valve stem of the oil quantity distribution mechanism and the inner convex ring of the valve seat of the reduction gearbox shaft, the oil inlet quantity of the middle axial oil hole is changed; it can meet the different requirements of the rotor assembly and the stator assembly for the cooling oil quantity under different working conditions of high and low speeds, so as to realize the real-time oil quantity distribution of the stator and the rotor. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The specification drawings forming a part of this application are used to provide a further understanding of this application. The schematic embodiments of this application and their descriptions are used to explain this application and do not constitute a limitation to this application.

[0021] Figure 1 It is a schematic structural diagram of the rotor assembly and its oil quantity distribution mechanism of the present utility model;

[0022] Figure 2 It is a sectional structural diagram of the rotor assembly and its oil quantity distribution mechanism of the present utility model;

[0023] Figure 3 It is a schematic structural diagram of the oil quantity distribution mechanism of the present utility model;

[0024] Figure 4 and Figure 5 are the exploded structural schematic diagrams of the rotor assemblies of the present utility model from two different angles;

[0025] Figure 6 is the front structural schematic diagram of the rotor baffle A of the present utility model;

[0026] Figure 7 is the reverse structural schematic diagram of the rotor baffle A of the present utility model;

[0027] Figure 8 is the structural schematic diagram of the rotating shaft of the present utility model.

[0028] The reference numerals are: 130, rotating shaft; 131, middle axial oil hole; 1311, side wall oil hole; 1312, bearing lubricating oil hole; 1313, limiting groove; 132, rotor iron core; 1321, rotor iron core axial oil passage; 133, rotor baffle A; 134, rotor baffle B; 135, injection hole B; 136, baffle radial oil passage A; 137, baffle radial oil passage B; 138, steel pressing ring; 140, installation chassis; 1401, support block; 141, valve rod; 1411, valve core; 1412, rack section; 142, counterweight ball; 143, spring; 144, worm; 145, limiting plate; 21, reduction gearbox shaft valve seat. Detailed implementation manners

[0029] It should be noted that the following detailed descriptions are all illustrative and are intended to provide further explanations for the present application. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by those of ordinary skill in the technical field to which the present application belongs.

[0030] It should be noted that the terms used herein are only for describing the specific implementation manners and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular forms are also intended to include the plural forms. In addition, it should be understood that when the terms "include" and / or "comprise" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0031] In addition, in the description of the present utility model, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation to the present utility model.

[0032] In addition, the terms "first" and "second" are only used for descriptive purposes and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, unless otherwise specified, the meaning of "a plurality" is two or more, unless otherwise clearly defined.

[0033] In the present utility model, unless otherwise clearly specified and defined, the terms such as "installation", "connection", "connection", "fixation", etc. should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0034] In the present utility model, unless otherwise clearly specified and defined, the first feature being "above" or "below" the second feature may include the direct contact between the first and second features, or may include the situation where the first and second features are not in direct contact but in contact through other features therebetween. Moreover, the first feature being "above", "over" and "on" the second feature includes that the first feature is directly above and obliquely above the second feature, or merely indicates that the horizontal height of the first feature is higher than that of the second feature. The first feature being "below", "under" and "beneath" the second feature includes that the first feature is directly below and obliquely below the second feature, or merely indicates that the horizontal height of the first feature is lower than that of the second feature.

[0035] The present utility model will be further described below in conjunction with the drawings and embodiments:

[0036] As Figures 1 to 3A variable-flow cooling structure for a motor rotor shown in the figure includes a rotating shaft 130 and a rotor core 132 fixedly sleeved on the rotating shaft 130. Rotor baffles A 133 and rotor baffles B 134 are respectively arranged at both ends of the rotor core 132. A plurality of axial oil channels 1321 of the rotor core are provided on the rotor core 132. A plurality of radial oil channels communicating with the axial oil channels 1321 of the rotor core are provided on the rotor baffles A 133 and rotor baffles B 134. The inside of the rotating shaft 130 is hollow to form a central axial oil hole 131. Side wall oil holes 1311 for communicating the central axial oil hole 131 with some of the radial oil channels are further provided on the side wall of the rotating shaft 130. The rotating shaft 130 is connected to a reduction gearbox shaft valve seat 21, and the rotating shaft 130 communicates with the reduction gearbox shaft valve seat 21. An oil quantity distribution mechanism is further provided on the rotor assembly. The oil quantity distribution mechanism includes a valve rod 141 arranged in the rotating shaft 130 and extending axially. The reduction gearbox shaft valve seat 21 is a hollow tubular shape, and an inner wall is provided with a convex ring 211. There are a plurality of the convex rings 211, and the inner diameters of the plurality of convex rings increase successively from the reduction gearbox cover end to the end cover end. A gap is provided between one end of the valve rod 141 and the inner wall of the convex ring 211. By changing the position of the valve rod 141, the gap becomes larger, and further the oil inflow of the central axial oil hole 131 increases. A bearing is further provided on the rotating shaft 130, and a bearing lubricating oil hole 1312 is further provided on one side of the rotating shaft 130 where the bearing is located. The bearing lubricating oil hole 1312 communicates with the central axial oil hole 131.

[0037] The oil quantity distribution mechanism further includes a mounting chassis 140 and a worm 144. A valve core 1411 is provided at one end of the valve rod 141. The other end of the valve rod 141 is a rack section 1412. A limiting groove 1313 is further provided on the inner wall of the rotating shaft 130. Protrusions are respectively provided at both ends of the valve rod 141 where the rack section 1412 is located. The protrusions are arranged in the limiting groove 1313 and slide in the limiting groove as the valve rod 141 moves.

[0038] The mounting chassis 140 is sleeved and fixed on the rotating shaft 130. Support blocks 1401 are provided on both sides of the rotating shaft 130 on the mounting chassis 140. The worm 144 penetrates through the support blocks 1401 and the rotating shaft 130, and the worm 144 meshes with the rack section 1412 of the valve rod 141 for transmission. A counterweight ball 142 is provided at one end of the worm 144, and a reset assembly is provided at the other end. When the rotor assembly rotates, the counterweight ball 142 drives the worm 144 to move radially under the action of centrifugal force, and further the valve rod 141 meshing with the worm 144 moves axially, so that the valve core 1411 moves away from the convex ring 211, and further the oil inflow of the central axial oil hole 131 increases.

[0039] The reset assembly is a limit plate 145 fixed to the other end of the worm 144, and a spring 143 sleeved on the worm 144 and abutting against the limit plate 145 and the support block 1401 at both ends. There are two worms 144, which are respectively located on both sides of the rack section 1412 and are both in meshing transmission with the rack section 1412. The counterweight balls 142 of the two worms 144 are respectively located on both sides of the rotating shaft 130.

[0040] The above structure enables the oil intake on the rotor assembly to automatically adjust the valve opening through the rotational speed of the rotor assembly, controlling the distribution ratio of the cooling lubricating oil. When the motor rotates, the faster the rotational speed of the rotating shaft, the greater the centrifugal force, the greater the displacement of the valve core, and the greater the oil intake. When the motor speed decreases, the centrifugal force decreases. Under the action of the reset spring, the worm resets and drives the valve stem to reset axially, the gap between the valve core and the convex ring resets, and the oil intake decreases.

[0041] As Figures 4 to 8 shown, oil injection holes B135 are provided on both the rotor baffle A133 and the rotor baffle B134. The radial oil passage includes a baffle radial oil passage A136 and a baffle radial oil passage B137, and the baffle radial oil passage A136 and the baffle radial oil passage B137 are arranged at equal intervals circumferentially. One end of the baffle radial oil passage A136 is communicated with the axial oil passage 1321 of the rotor core, and the other end is communicated with the oil injection hole B135. One end of the baffle radial oil passage B137 is communicated with the axial oil passage 1321 of the rotor core, and the other end is communicated with the side wall oil hole 1311. The positions of the baffle radial oil passages A136 on the rotor baffle A133 and the rotor baffle B134 are staggered with each other.

[0042] One end of the rotating shaft 130 is provided with a shaft shoulder. The rotor baffle B134 abuts against the shaft shoulder. One side of the rotor baffle A133 abuts against the rotor core 132, and the other side is axially limited by a steel pressing ring 138 that is in interference fit with the rotating shaft 130.

[0043] The above oil flow form from the rotating shaft to the rotor baffle realizes a two-way cross oil passage by rotating the angle of the rotor baffle. Finally, it is sprayed into the inner circle of the wire coil from the rotor baffle, and there is also a path that can be distributed to the bearing, which not only satisfies the cooling of the rotor core, but also cools the stator wire coil and takes into account the lubrication of the bearing.

[0044] The rotor cooling path of the present utility model realizes the oil quantity balance of the rotor through the reduction gearbox shaft valve seat and the rotating shaft, in combination with the oil quantity distribution mechanism, meeting the real-time oil quantity adaptability adjustment of the rotor oil quantity under low-speed, medium-speed to high-speed working conditions. After passing through the oil quantity distribution mechanism, the cooling oil realizes a two-way cross passage inside the rotor core by means of the ingenious structure of the rotor baffle, and finally can also be sprayed to the inner sides of the two end wire coils through the outside of the rotor baffle, realizing full-range cooling of the wire coil.

[0045] In the description of this specification, the descriptions referring to terms such as "one embodiment", "some embodiments", "examples", "specific examples", or "some examples", etc. mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present utility model. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0046] Although the embodiments of the present utility model have been shown and described above, it can be understood that the above embodiments are exemplary and should not be construed as limitations on the present utility model. Those of ordinary skill in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present utility model without departing from the principles and purposes of the present utility model. Any simple modification, equivalent change, and modification made to the above embodiments based on the technical essence of the present utility model still fall within the scope of the technical solution of the present utility model.

Claims

1. A variable-flow cooling structure for a motor rotor, comprising a rotating shaft (130) and a rotor core (132) fixedly sleeved on the rotating shaft (130), characterized in that: At both ends of the rotor core (132), a rotor baffle A (133) and a rotor baffle B (134) are respectively provided. A plurality of axial oil passages (1321) of the rotor core are provided on the rotor core (132). A plurality of radial oil passages communicating with the axial oil passages (1321) of the rotor core are provided on the rotor baffle A (133) and the rotor baffle B (134). The inside of the rotating shaft (130) is hollow to form a central axial oil hole (131). A side wall oil hole (1311) for communicating the central axial oil hole (131) with some of the radial oil passages is further provided on the side wall of the rotating shaft (130). The rotating shaft (130) is connected to a reduction gearbox shaft valve seat (21), and the rotating shaft (130) communicates with the reduction gearbox shaft valve seat (21). A fuel quantity distribution mechanism is further provided on the rotor assembly. The fuel quantity distribution mechanism includes a valve rod (141) arranged inside the rotating shaft (130) and extending axially. The reduction gearbox shaft valve seat (21) is a hollow tubular shape, and an inner wall is provided with a convex ring (211). A gap is provided between one end of the valve rod (141) and the inner wall of the convex ring (211). By changing the position of the valve rod (141), the gap becomes larger, and thus the fuel intake of the central axial oil hole (131) increases.

2. The variable-flow cooling structure of an electric motor rotor according to claim 1, wherein: There are a plurality of the convex rings (211), and the inner diameters increase successively along the moving direction of the valve rod (141).

3. The variable flow cooling structure of a motor rotor according to claim 1, characterized in that: The fuel quantity distribution mechanism further includes a mounting chassis (140) and a worm (144). A valve core (1411) is provided at one end of the valve rod (141). The other end of the valve rod (141) is a rack section (1412). The mounting chassis (140) is sleeved and fixed on the rotating shaft (130). Support blocks (1401) are provided on both sides of the rotating shaft (130) on the mounting chassis (140). The worm (144) passes through the support blocks (1401) and the rotating shaft (130), and the worm (144) meshes with the rack section (1412) of the valve rod (141) for transmission. A counterweight ball (142) is provided at one end of the worm (144), and a reset assembly is provided at the other end. When the rotor assembly rotates, the counterweight ball (142) drives the worm (144) to move radially under the action of centrifugal force, and further makes the valve rod (141) meshing with the worm (144) move axially, so that the valve core (1411) moves away from the convex ring (211), and thus the fuel intake of the central axial oil hole (131) increases.

4. The variable-flow cooling structure of an electric motor rotor according to claim 3, wherein: There are two worms (144), which are respectively located on both sides of the rack section (1412), and both mesh with the rack section (1412) for transmission. The counterweight balls (142) of the two worms (144) are respectively located on both sides of the rotating shaft (130).

5. The variable flow cooling structure of an electric motor rotor according to claim 3, characterized in that: A limiting groove (1313) is further provided on the inner wall of the rotating shaft (130). Protrusions are respectively provided at both ends of the rack section (1412) on the valve rod (141). The protrusions are arranged in the limiting groove (1313) and slide in the limiting groove as the valve rod (141) moves.

6. The variable flow cooling structure of a motor rotor according to claim 1, wherein: The rotor baffle A (133) and the rotor baffle B (134) are both provided with oil injection holes B (135). The radial oil passage includes a baffle radial oil passage A (136) and a baffle radial oil passage B (137). One end of the baffle radial oil passage A (136) is communicated with the axial oil passage of the rotor core (1321), and the other end is communicated with the oil injection hole B (135). One end of the baffle radial oil passage B (137) is communicated with the axial oil passage of the rotor core (1321), and the other end is communicated with the side wall oil hole (1311).

7. The variable flow rate cooling structure for a motor rotor according to claim 6, wherein: The baffle radial oil passage A (136) and the baffle radial oil passage B (137) are arranged at uniform intervals in the circumferential direction, and the positions of the baffle radial oil passage A (136) on the rotor baffle A (133) and the rotor baffle B (134) are staggered with each other.

8. A variable flow rate cooling structure for an electric motor rotor according to claim 6, characterized in that: The oil injection hole B (135) is close to the outer edge of the rotor baffle A (133) or the rotor baffle B (134), and the oil injection hole B (135) is inclined from inside to outside.

9. The variable flow cooling structure of an electric motor rotor according to claim 1, wherein: A bearing is further provided on the rotating shaft (130), and a bearing lubricating oil hole (1312) is provided on one side of the rotating shaft (130) where the bearing is located. The bearing lubricating oil hole (1312) is communicated with the middle axial oil hole (131).

10. A variable-flow cooling structure for a motor rotor according to claim 1, characterized in that: One end of the rotating shaft (130) is provided with a shaft shoulder. The rotor baffle B (134) abuts against the shaft shoulder. One side of the rotor baffle A (133) abuts against the rotor core (132), and the other side is axially limited by a steel pressing ring (138) which is in interference fit with the rotating shaft (130).

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