A motor for a window lifter of an automobile, a window lifter of an automobile, and an automobile

Abstract

The present invention provides a motor for an automobile window lifter, an automobile window lifter, and an automobile. The motor includes a rotor, a worm wheel, a worm, and a transmission shaft. The worm wheel is sleeved and fixed on the transmission shaft and meshes with the worm wheel. When the rotor rotates, the worm wheel and the worm wheel are driven to run through the transmission shaft, so that the worm wheel drives the window glass to move up and down through the output teeth. Lubricating grease is provided on the meshing surfaces of the worm wheel and the worm wheel. The static friction coefficient of the lubricating grease is μm. 油‑静设计 At 0.24~0.2; the technical solution provided by the present invention can effectively ensure the self-locking function of the automobile window lifter, easily realize self-locking control, improve transmission efficiency, enable the automobile window lifter to achieve a better lightweight design, reduce costs, and improve the grade of the automobile.

Description

Technical Field

[0001] The present invention belongs to the technical field of automobile window lifter motors, and in particular relates to an automobile window lifter motor, an automobile window lifter, and an automobile. Background Art

[0002] Currently, the window-holding function can be divided into two categories: "holding the window at the top" (when the window is fully closed) and "holding the window in the middle" (between when the window is fully raised and fully lowered). This is primarily achieved by the motor and lifter working together with the door sealing system. To achieve this, the motor (without power and with the power pins shorted) generates friction at various friction interfaces (typically the bearings and worm gear) to produce a torque (self-locking) that resists the rotation of the output teeth. This friction changes with the motor's operating cycle, so the self-locking torque also changes to maintain the "window-holding" function. The mainstream solution is to reduce the lead angle or increase the surface roughness of the worm gear and bearings to increase their friction coefficient.

[0003] Among the existing technologies, Patent 1 (CN1808855A) mentions designing the lead angle (i.e., helix angle) to 3 degrees to 3 degrees 30 minutes to achieve self-locking performance. Patent 2 (CN108603544A) uses a segmented shaft design, with the two end shafts forming a one-way clutch. This design does not rely on the lead angle of the worm gear, but instead uses a mechanical one-way clutch locking mechanism. The low lead angle design results in low forward transmission efficiency of the motor, as the forward transmission efficiency of the motor is proportional to the lead angle of the worm gear. The solution mentioned in Patent 1 (CN1808855A) results in low transmission efficiency of the motor system, requiring more iron or copper wire to increase the motor's torque, which is not conducive to lightweight and low cost. The self-locking design of the one-way clutch segmented shaft used in Patent 2 (CN108603544A) increases the number of parts and design cost, increasing the risk of failure. Other manufacturers have adopted an increased friction coefficient between the shaft and the bearing, which is difficult to control and increases the risk of the window glass not being able to lower.

[0004] Based on the technical problems existing in the above-mentioned automobile window lifter motor, there is no relevant solution yet; therefore, it is urgent to find an effective solution to solve the above-mentioned problems. Summary of the Invention

[0005] The purpose of the present invention is to address the deficiencies in the above-mentioned technologies and to propose a car window lifter motor, a car window lifter and a car, aiming to solve the problem that the existing car window lifter has a better self-locking function or transmission design.

[0006] The present invention provides a motor for an automobile window lifter, the motor comprising a rotor, a worm wheel, a worm, and a transmission shaft; the worm wheel is sleeved and fixed on the transmission shaft and meshes with the worm wheel; when the rotor rotates, the worm wheel and the worm wheel are driven to run through the transmission shaft, so that the worm wheel drives the window glass to move up and down through the output teeth; lubricating grease is provided on the meshing surfaces of the worm wheel and the worm wheel, and the static friction coefficient of the lubricating grease is μ 油-静 It is designed to be between 0.24 and 0.26, so that the operating efficiency η2 of the worm gear driving the worm is less than 0% or the operating efficiency η1 of the worm gear driving the worm gear is greater than 0%.

[0007] Furthermore, the worm is provided with an engaging thread, and the worm is engaged with the gear of the worm wheel through the engaging thread; the lead angle γ of the engaging thread is designed to be between 3.7° and 4.1°.

[0008] Furthermore, the static friction coefficient μ of the lubricating grease 油-静 and the motor static friction coefficient μ' 电机-静 Satisfies the following formula:

[0009] μ' 电机-静 =μ 油-静 *μ JZ ;μ JZ is the correction coefficient, correction coefficient μ JZ The selected value is 0.3~0.4.

[0010] Furthermore, the pressure angle α of the worm gear is designed to be between 6° and 15°.

[0011] Furthermore, the static friction coefficient μ of the lubricating grease 油-静 Design ambient temperature ≤80°.

[0012] Furthermore, the operating efficiency η1 of the worm-driven worm wheel satisfies the following formula:

[0013] ;

[0014] The operating efficiency η2 of the worm gear drive worm satisfies the following formula:

[0015] ; Wherein, α is the pressure angle, γ is the lead angle; μ is the friction coefficient, the friction coefficient μ is designed to μ' 电机-静 To calculate.

[0016] Furthermore, the stall torque T k Satisfaction: T K = T FS *R*η1;T K is the stall torque of the motor with reduction gearbox; T FS is the stall torque of a single motor; R is the reduction ratio of the motor's reduction gearbox.

[0017] Furthermore, the operating efficiency η2 of the worm gear driving the worm is less than 0% or the operating efficiency η1 of the worm gear driving the worm gear is greater than 0%, thereby maintaining the self-locking function when the motor drives the vehicle window glass to move up and down.

[0018] Furthermore, the motor also includes a gear box and a metal casing, and the gear box is fixedly connected to the metal casing; the worm wheel is a POM worm wheel, the worm is a metal worm, and the transmission shaft is a metal shaft; one end of the metal shaft passes through the first oil-containing bearing and is rotatably arranged at one end in the metal casing; the other end of the metal shaft passes through the third oil-containing bearing and is rotatably arranged at the other end in the metal casing; the third oil-containing bearing is arranged in a plastic bearing fixing seat, and the plastic bearing fixing seat is arranged on the protruding inner wall of the other end in the metal casing; the middle section of the metal shaft passes through the second oil-containing bearing, the second oil-containing bearing is arranged in the brush holder box, and is located in the metal casing; the POM worm wheel can be rotatably arranged in the gear box and is transmission-connected to the rotor; the metal worm is arranged between the first oil-containing bearing and the second oil-containing bearing.

[0019] Correspondingly, in combination with the above solution, the present invention further provides an automobile window lifter, comprising a drive motor, which is the automobile window lifter motor described above.

[0020] Correspondingly, in combination with the above solution, the present invention further provides an automobile, comprising an automobile window lifter; the automobile window lifter is the automobile window lifter described above.

[0021] The technical solution provided by the present invention can effectively ensure the self-locking function of the automobile window lifter, easily realize self-locking control, improve transmission efficiency, enable the automobile window lifter to achieve a better lightweight design, reduce costs, and improve the grade of the automobile. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0023] The present invention will be further described below with reference to the accompanying drawings:

[0024] Figure 1 This is a cross-sectional view of a motor for an automobile window lifter according to the present invention;

[0025] Figure 2 This is a schematic diagram of the worm gear surface of the present invention;

[0026] Figure 3 This is a schematic diagram of the grease transmission efficiency test of the present invention.

[0027] In the figure: 1. Worm gear; 2. Worm; 3. Drive shaft; 4. First oil-containing bearing; 5. Second oil-containing bearing; 6. Third oil-containing bearing; 7. Gear box; 8. Brush holder box; 9. Plastic bearing fixing seat; 10. Metal casing. DETAILED DESCRIPTION

[0028] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0029] It should be noted that when an element is referred to as being “fixed on” or “disposed on” another element, it may be directly on the other element or indirectly on the other 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.

[0030] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Thus, a feature specified as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "plurality" means two or more, unless otherwise specifically defined. "Several" means one or more, unless otherwise specifically defined.

[0031] In the description of the present invention, it should be understood that the terms "up", "down", "front", "back", "left", "right", etc., indicating directions or positional relationships, are based on the directions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore cannot be understood as a limitation on the present invention.

[0032] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and may encompass internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0033] As shown in Figure 1 to Figure 2As shown, the present invention provides a motor for an automobile window lifter, the motor comprising a rotor, a worm wheel 1, a worm 2, and a transmission shaft 3; wherein the worm 2 is sleeved and fixed on the transmission shaft 3 and can rotate together with the transmission shaft 3; further, the worm 2 and the worm wheel 1 are meshed with each other, thereby realizing a transmission connection; when the rotor rotates, the worm 2 and the worm wheel 1 are driven to operate through the transmission shaft 3, so that the worm wheel 1 drives the window glass to move up and down through the output teeth; further, lubricating grease is provided on the meshing surfaces of the worm 2 and the worm wheel 1, and the static friction coefficient of the lubricating grease is μ 油-静 Designed to be between 0.24 and 0.26, so that the operating efficiency η2 of the worm wheel 1 driving the worm 2 is less than 0% or the operating efficiency η1 of the worm 2 driving the worm wheel 1 is greater than 0%, thereby maintaining the self-locking function; Specifically, in the present application, the static friction coefficient μ of the lubricating grease is 油-静 The design ambient temperature is ≤80°C, that is, the static friction coefficient of the lubricating grease can be maintained between 0.24 and 0.26 when the ambient temperature is ≤80°C, which fully meets the requirements for the operation of the automobile window lifter at high temperatures and realizes the self-locking function; the automobile window lifter motor provided by the present invention enables the automobile window lifter to have a better transmission design and ensures the self-locking performance of the automobile window lifter.

[0034] Preferably, in combination with the above scheme, as shown in Figures 1 to Figure 2 As shown, the worm 2 is provided with an engaging thread, so that the worm 2 can mesh with the gear of the worm wheel 1 through its engaging thread to achieve a transmission connection; specifically, in the present application, the lead angle γ of the engaging thread is designed to be between 3.7° and 4.1°. This design is based on the fact that the design of the lead angle γ can directly affect the transmission efficiency between the worm wheel and the worm, so that the automobile window lifter can have a better transmission design and ensure the self-locking performance of the automobile window lifter.

[0035] Preferably, in combination with the above scheme, as shown in Figures 1 to Figure 2 As shown, the static friction coefficient of lubricating grease μ 油-静 and the motor static friction coefficient μ' 电机-静 Satisfies the following formula:

[0036] μ' 电机-静 =μ 油-静 *μ JZ ; where μ JZ is the correction coefficient, the correction coefficient μ JZ The selected value is 0.3~0.4, the correction coefficient μ JZ The value of is based on the design obtained in actual research, which can completely correct the friction coefficient between the worm gear and the worm, so that the static friction coefficient of the lubricating grease μ 油-静 The design is between 0.24 and 0.26, so that the automobile window lifter can have a better transmission design and ensure the self-locking performance of the automobile window lifter.

[0037] Preferably, in combination with the above scheme, as shown in Figures 1 to Figure 2 As shown in the figure, the pressure angle α of the worm gear 1 is designed to be between 6° and 15°. It should be explained that in the above practical application research conditions, although the pressure angle α is not the main factor affecting the efficiency of the worm gear transmission, it can match the static friction coefficient μ of the above lubricating grease within the design range of 6° to 15°. 油-静 and lead angle γ to achieve the transmission efficiency of the worm gear and realize the self-locking function.

[0038] Preferably, in combination with the above scheme, as shown in Figures 1 to Figure 2 As shown, the operating efficiency η1 of the worm 2 driving the worm wheel 1 satisfies the following formula:

[0039] ;

[0040] The operating efficiency η2 of worm wheel 1 driving worm 2 satisfies the following formula:

[0041] Wherein, α is the pressure angle, γ is the lead angle, μ is the friction coefficient, and the friction coefficient μ is designed to be μ' 电机-静 To calculate, that is, to achieve correction through the correction system, to achieve more accurate conversion.

[0042] Preferably, in combination with the above scheme, as shown in Figures 1 to Figure 2 As shown, the motor's stall torque T k Satisfaction: T K = T FS *R*η1; where T K is the stall torque of the motor with reduction gearbox; T FS is the stall torque of a single motor; R is the reduction ratio of the motor's reduction gearbox; further, when T FS =0.35Nm, when R:84, 0.35*84*2.6%=0.76Nm, and the motor needs to be increased by 0.76Nm, which is 7% higher than the original motor torque. The improvement in efficiency can save the cost of magnet grade or increase the outer diameter of the coil, and is also conducive to the lightweight design of the motor.

[0043] Preferably, in combination with the above scheme, as shown in Figures 1 to Figure 2As shown, in the present application, the vehicle window is raised and lowered by a motor and a lifter, and at the same time, an anti-theft function needs to be met, that is, to prevent people outside the vehicle from pressing the glass down with their hands to take items inside the vehicle; the anti-theft function requires that the motor has a self-locking performance, that is, the theoretical operating efficiency η2 of the worm wheel 1 driving the worm 2 is less than 0% or the operating efficiency η1 of the worm 2 driving the worm wheel 1 is greater than 0%, so that the motor maintains the self-locking function when driving the vehicle window glass up and down; specifically, the self-locking force can usually be met at room temperature, but at high temperatures (over 60°C), due to the decrease in grease viscosity, the friction coefficient decreases, and the motor operating efficiency increases, resulting in the motor being unable to self-lock, and the key parameters are the lead angle of the worm wheel and the dynamic and static friction coefficients of the grease; the present invention will use the static friction coefficient of the grease to infer the reverse operating efficiency of the entire motor and predict the motor's self-locking ability. Combined with a larger lead angle design, it takes into account both efficient forward transmission efficiency and high-performance reverse self-locking performance, and can achieve self-locking function at temperatures as high as 80°C.

[0044] Preferably, in combination with the above scheme, as shown in Figures 1 to Figure 2 As shown, the motor also includes a gear box 7 and a metal casing 10, wherein the gear box 7 is fixedly connected to the metal casing 10 to form an integrated structure; the worm wheel 1 is a POM worm wheel, the worm 2 is a metal worm, and the transmission shaft 3 is a metal shaft, which is transmission-connected to the rotor of the motor, so that the rotor can drive the metal shaft to rotate; specifically, one end of the metal shaft passes through the first oil-containing bearing 4 and can rotate to the end set in the metal casing 10; the other end of the metal shaft passes through the third oil-containing bearing 6 and can rotate to the other end set in the metal casing 10; the third oil-containing bearing 6 is a metal shaft. The bearing 6 is arranged in the plastic bearing fixing seat 9, and the plastic bearing fixing seat 9 is arranged on the inner wall protruding at the other end of the metal housing 10; the middle section of the metal shaft passes through the second oil-containing bearing 5, and the second oil-containing bearing 5 is arranged in the brush holder box 8 and is located in the metal housing 10; adopting the above scheme, the metal shaft is supported by three oil-containing bearings to meet the transmission efficiency requirements; the POM worm wheel can be rotatably arranged in the gear box 7 and is connected to the rotor transmission; the metal worm is arranged between the first oil-containing bearing 4 and the second oil-containing bearing 5; specifically, as Figure 1 It can be seen that when the rotor rotates, the metal shaft drives the worm and worm wheel to operate, and the worm wheel drives the glass to move up and down through the output teeth; during the rotation of the rotor, the metal shaft and the three bearings (the first oil-containing bearing 4, the second oil-containing bearing 5, and the third oil-containing bearing 6) have friction motion, and the stability of its friction coefficient depends on the geometric tolerances and surface roughness of the components. The solution of the present invention focuses on the impact of the friction coefficient of the worm wheel on the overall transmission efficiency.

[0045]

[0046] It can be seen from Table 1 above that when the pressure angle α increases rapidly from 6° to 15°, the worm gear transmission efficiency decreases from 53.3% to 52.4%, and the reversal efficiency decreases from -0.7% to -3.6%. The change rate is very small and can be understood as a non-critical factor, but it can ensure the transmission efficiency of the worm gear, thereby enabling the motor to achieve self-locking.

[0047]

[0048] From Table 2 above, we can see that when γ=3.69°, α=10°, and μ=0.064, η2<0%, and the motor can be locked. Further analysis shows that when μ decreases from 0.064 to 0.06, η2=5.5%. When μ further decreases to 0.055, η2 quickly increases to 13.4%, indicating that the change in the friction coefficient μ is very sensitive to the reverse transmission efficiency of the worm gear and is a key factor.

[0049]

[0050] It can be seen from Table 3 that when α=10°, μ=0.064, and γ=3~3.7°, η2<0%, and the smaller γ is, the lower the transmission efficiency is, that is, the better the self-locking performance is; when γ continues to decrease to 3°, η2=-23.9%, indicating that the lead angle has a greater impact on the reversal efficiency of the worm gear and is a key factor.

[0051] Further, Figure 3 Specifically, the effect of different loads on the grease friction coefficient was tested. The grease transmission efficiency test conditions were: POM cylinder, S45C Rz0.2 iron plate, speed 5 mm / s, temperature: 80°C, and pressure: 1 kg / 7 kg. The specific results are shown in Table 4 below:

[0052]

[0053] As shown in Table 4, when the load increases, both the dynamic and static friction coefficients tend to decrease. When the load increases, the friction coefficient decreases, and the motor is more likely to experience self-locking force failure. When conducting performance comparison tests, it is necessary to consider using the same load.

[0054] In combination with the above scheme, when designing the motor self-locking force test, first, according to Table 1, it can be seen that the difference between the pressure angle of 10° and 12° has very little effect on the forward and reverse rotation efficiency of the worm gear; according to Tables 2 and 3, the lead angle and friction coefficient are key factors in the forward and reverse rotation efficiency. Therefore, this application scheme designs two motors with different lead angles, named JC-A and JC-B respectively:

[0055] Motor JC-A: pressure angle 10°, lead angle 3.69°;

[0056] Motor JC-B: pressure angle 12°, lead angle 4.2°;

[0057] JC-A and JC-B are paired with three mass-produced greases. YZ001-003 are existing greases, while YZ-004 is a grease required by new technology to meet the requirements of large lead angle designs. The dynamic and static friction coefficients of the greases were designed for a temperature of 80°C and measured under the same conditions. The following five samples were created by combining three motors with four greases, namely JC-01# to JC-05#:

[0058] YZ-001#: μ moving = 0.07, μ static = 0.165;

[0059] YZ-002#: μ moving = 0.085, μ static = 0.24;

[0060] YZ-003#: μ moving = 0.055, μ static = 0.225;

[0061] YZ-004#: μ moving = 0.055, μ static = 0.265;

[0062]

[0063] During the test, the motor is kept at 80°C for 2 hours, a 15Nm load is applied to the worm gear output teeth, and the worm gear rotation angle is recorded. If the worm gear rotation angle is greater than 90 degrees, it is considered to have slipped and cannot self-lock, and the slip torque is recorded. Since the motor is stationary at this time, its static friction coefficient is the main parameter. At this time, only the static friction coefficient of the grease under specific conditions is known, and the static friction coefficient of the motor system is unknown. At this time, a friction coefficient correction factor μ is required. JZ This coefficient corrects the relevant friction coefficient during the operation of the motor, as shown in the formula μ' 电机-静 =μ 油-静 *μ JZ As shown; the premise is that the roughness and form and position tolerance accuracy of the shaft, bearing, worm, worm wheel and gear box and the related moving surfaces are high and remain stable; therefore, the corrected μ' 电机-静 It can be used as the static friction coefficient μ in the above transmission efficiency formula, specifically:

[0064] μ 电机-静 Substitute into the formula Finally, the calculated value of η'2 is obtained, and then the calculated value is compared with the measured value (the measured output tooth rotation angle); when the measured self-locking angle is <10°, the motor meets the self-locking requirements, that is, *η'2<0%, otherwise, its *η'2>0%;

[0065] As shown in Table 5, only the measured self-locking angle of sample JC-01# is less than 10°, while samples JC-02# and JC-04# have already slipped. The self-locking angle of sample JC-03# is greater than 10°, which is close to the limit and the design margin is insufficient.

[0066] μ' 电机-静 Substitute into the formula Finally, η'2 is obtained, and then η'2 is compared with *η'2. The theoretical prediction values of the four motors are consistent with the measured results;

[0067] From the above analysis, we can see that when the lead angle of the motor is 4.2°, the current grease has a great risk of not being able to meet the self-locking function. Therefore, the formula μ' can be used 电机-静 =μ 油-静 *μ JZ The lead angle and grease static friction coefficient were redesigned, and the corrected μ' 电机-静 It can be used as the static friction coefficient μ in the above transmission efficiency formula.

[0068] JC-05# is a newly designed motor, and YZ-004 grease is a newly designed grease. The static friction coefficient of the grease needs to be increased to 0.25, and the lead angle is 4°. Under this combination, the reverse operation efficiency of the motor is -8.6%, and high-temperature self-locking can be achieved.

[0069] The design of the JC-05# sample changes the motor lead angle from the original 3.69° to 4°, and its forward transmission efficiency is increased from 49% to 51.6%.

[0070] Accordingly, in combination with the above scheme, as shown in Figures 1 to Figure 2 As shown, the present invention also provides an automobile window lifter, including a drive motor, wherein the drive motor is the automobile window lifter motor described above; by adopting the automobile window lifter motor described above, the automobile window lifter can maintain its own function under high temperature conditions.

[0071] Accordingly, in combination with the above scheme, as shown in Figures 1 to Figure 2 As shown, the present invention also provides a car, including a car window lifter, and the car window lifter is the car window lifter described above; using the above-mentioned car window lifter can effectively improve the self-locking experience of the car window glass lifting and lowering, and improve the grade of the car.

[0072] The technical solution provided by the present invention can effectively ensure the self-locking function of the automobile window lifter, easily realize self-locking control, improve transmission efficiency, enable the automobile window lifter to achieve a better lightweight design, reduce costs, and improve the grade of the automobile.

[0073] The above description is merely a preferred embodiment of the present invention and does not constitute any form of limitation to the present invention. Any person skilled in the art can, without departing from the scope of the technical solution of the present invention, make many possible changes and modifications to the technical solution of the present invention using the above technical content, or modify it into an equivalent embodiment with equivalent changes. Therefore, any changes, modifications, equivalent changes, and modifications made to the above embodiments based on the technology of the present invention without departing from the content of the technical solution of the present invention shall fall within the scope of protection of the present technical solution.

Claims

1. A car window lifter motor, characterized in that: The motor comprises a rotor, a worm wheel (1), a worm (2) and a transmission shaft (3); the worm (2) is sleeved and fixed on the transmission shaft (3) and meshes with the worm wheel (1); when the rotor rotates, it drives the worm (2) and the worm wheel (1) to run through the transmission shaft (3), so that the worm wheel (1) drives the window glass to move up and down through the output teeth; lubricating grease is provided on the meshing surfaces of the worm (2) and the worm wheel (1), and the static friction coefficient of the lubricating grease is μ 油-静 The static friction coefficient μ of the lubricating grease is designed to be between 0.24 and 0.

26. 油-静 Design ambient temperature ≤ 80°; static friction coefficient of the lubricating grease μ 油-静 and the motor static friction coefficient μ' 电机-静 Satisfies the following formula: μ' 电机-静 =μ 油-静 *μ JZ ; The μ JZ is the correction coefficient, the correction coefficient μ JZ The selected value is 0.3~0.4; the worm is provided with a meshing thread, and the worm is meshed with the gear of the worm wheel through the meshing thread; the lead angle γ of the meshing thread is designed to be between 3.7°~4.1°; the pressure angle α of the gear of the worm wheel (1) is designed to be between 6°~15°.

2. The automobile window lifter motor according to claim 1, characterized in that: The operating efficiency η1 of the worm (2) driving the worm wheel (1) satisfies the following formula: ； The operating efficiency η2 of the worm wheel (1) driving the worm (2) satisfies the following formula: ; The α is the pressure angle; the γ is the lead angle; the μ is the friction coefficient, the friction coefficient μ is designed to μ' 电机-静 To calculate.

3. The automobile window lifter motor according to claim 2, characterized in that: The stall torque T of the motor k Satisfaction: T K = T FS *R*η1;T K is the stall torque of the motor with reduction gearbox; T FS is the stall torque of a single motor; R is the reduction ratio of the reduction gearbox of the motor.

4. The automobile window lifter motor according to claim 2, characterized in that: The operating efficiency η2 of the worm wheel (1) driving the worm (2) is less than 0%, or the operating efficiency η1 of the worm (2) driving the worm wheel (1) is greater than 0%, so that the motor maintains a self-locking function when driving the vehicle window glass to move up and down.

5. The automobile window lifter motor according to claim 1, characterized in that: The motor further comprises a gear box (7) and a metal housing (10), wherein the gear box (7) is fixedly connected to the metal housing (10); the worm wheel (1) is a POM worm wheel, the worm (2) is a metal worm, and the transmission shaft (3) is a metal shaft; one end of the metal shaft passes through a first oil-containing bearing (4) and is rotatably disposed in the metal housing (10); the other end of the metal shaft passes through a third oil-containing bearing (6) and is rotatably disposed in the metal housing (10); the third oil-containing shaft The bearing (6) is arranged in a plastic bearing fixing seat (9), and the plastic bearing fixing seat (9) is arranged on the inner wall protruding from the other end of the metal housing (10); the middle section of the metal shaft passes through the second oil-containing bearing (5), and the second oil-containing bearing (5) is arranged in the brush holder box (8) and is located in the metal housing (10); the POM worm wheel is rotatably arranged in the gear box (7) and is transmission-connected to the rotor; the metal worm is arranged between the first oil-containing bearing (4) and the second oil-containing bearing (5).

6. An automobile window lifter, comprising a drive motor, characterized in that: The driving motor is the automobile window lifter motor according to any one of claims 1 to 5.

7. An automobile, comprising an automobile window regulator; characterized in that: The automobile window lifter is the automobile window lifter according to claim 6.

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