阅读说明：本技术 一种高啮合成功概率的齿式离合器 (Tooth clutch with high meshing success probability ) 是由 闫泽 陈克鑫 王学志 战庆欣 戴维泽 曲盛楠 魏君波 张祥 王春玲 于 2020-12-25 设计创作，主要内容包括：本发明提供一种高啮合成功概率的齿式离合器,在动套齿和静套齿的轮齿端面上,靠近非传扭齿面的一侧制成一段斜面,靠近传扭齿面的一侧保留直面,斜面宽度约占齿厚的95％。动套齿齿端面斜面的倾斜方向与动套齿的移动方向相反,静套齿齿端面斜面的倾斜方向与动套齿的移动方向相同,动、静套齿的齿端面斜面倾斜角相等。啮合时,动套齿在外力作用下移向静套齿,动、静套齿的齿端面斜面相互接触,随着动套齿的转动,由于斜面的作用,动套齿相对静套齿产生了轴向移动距离L,当动套齿的轮齿转过与之相接触的当前静套齿轮齿,并与下一个静套齿轮齿的工作齿面接触时,距离L可避免打齿现象发生,提高了套齿一次啮合成功的概率,并且套齿保持传扭强度不下降。(The invention provides a tooth clutch with high meshing success probability, wherein a section of inclined surface is formed on one side close to a non-torque transmission tooth surface on the gear tooth end surfaces of a movable sleeve gear and a fixed sleeve gear, a straight surface is reserved on one side close to a torque transmission tooth surface, and the width of the inclined surface accounts for about 95% of the tooth thickness. The inclined direction of the end face inclined plane of the movable sleeve tooth is opposite to the moving direction of the movable sleeve tooth, the inclined direction of the end face inclined plane of the static sleeve tooth is the same as the moving direction of the movable sleeve tooth, and the inclined angles of the end face inclined planes of the movable sleeve tooth and the static sleeve tooth are equal. When meshing, the movable sleeve gear moves towards the static sleeve gear under the action of external force, the end face inclined planes of the movable sleeve gear and the static sleeve gear are in mutual contact, along with the rotation of the movable sleeve gear, the movable sleeve gear generates an axial movement distance L relative to the static sleeve gear due to the action of the inclined planes, when the gear tooth of the movable sleeve gear rotates over the current static sleeve gear tooth in contact with the movable sleeve gear and is in contact with the working tooth face of the next static sleeve gear tooth, the distance L can avoid the gear beating phenomenon, the probability of one-time meshing success of the sleeve gear is improved, and the sleeve gear keeps the torque transmission strength from being reduced.)

1. A high meshing success probability tooth clutch comprising an input assembly (100), a slip assembly (200), and an output assembly (300), characterized in that: the input assembly (100) is provided with an external spiral structure (110), the sliding assembly (200) is provided with a movable sleeve gear (220) and an internal spiral mechanism (210), the output assembly (300) is provided with a static sleeve gear (320), the external spiral structure is connected with the internal spiral mechanism, the static sleeve gear is meshed with the movable sleeve gear, one side of the end surface of the movable sleeve gear, which is close to a non-torque transmission gear surface, is provided with a section of inclined surface, one side of the end surface of the movable sleeve gear, which is close to a torque transmission gear surface, is provided with a straight surface, the inclined direction of the inclined surface of the end surface of the movable sleeve gear is opposite to; a section of inclined surface is formed on one side, close to the non-torque transmission tooth surface, of the end surface of the fixed sleeve tooth, a straight surface is reserved on one side, close to the torque transmission tooth surface, the inclined direction of the inclined surface of the end surface of the fixed sleeve tooth is the same as the moving direction of the movable sleeve tooth, and the inclined angle is beta.

2. A high meshing success probability tooth clutch according to claim 1, characterized in that: the width of the straight surface of the movable sleeve tooth and the width of the inclined surface of the fixed sleeve tooth are both 5% of the tooth thickness, and the width of the inclined surface is 95% of the tooth thickness.

3. A high meshing success probability tooth clutch according to claim 1 or 2, characterized in that: after the positioning surface (205) of the sliding component is tightly pressed with the positioning surface (120) of the input component, the torque is transmitted to the output component through the sliding component by the input component.

Technical Field

The invention relates to a tooth clutch with high meshing success probability, and a tooth end structure for improving the meshing success probability of the clutch.

Background

At present, the torque transmission teeth of the known gear clutch generally adopt involute tooth profiles, the tooth profile pressure angle is generally 15-35 degrees, the gear clutch has automatic centering capacity due to the existence of the pressure angle, the involute tooth profiles are basically consistent with the processing technology of gear teeth of a gear, and the processing is very convenient, so that the gear clutch adopting the involute tooth profiles is widely applied compared with the gear profiles of gear teeth. The tooth clutch generates tooth side clearance in a tooth thickness reduction mode, and is convenient for axial meshing of the torque transmission sleeve teeth. In order to ensure the bending and shearing strength of the torque transmission sleeve teeth, the reduction amount of the tooth thickness is limited to be about 5% -10% of the tooth pitch, and the tooth side gap is smaller relative to the tooth pitch size, so that the meshing success probability of the tooth clutch is lower, and particularly in the automatic control tooth clutch which adopts spiral motion to realize tooth meshing, when the rotation speed difference is larger, the lower meshing success probability is easy to cause tooth beating, so that the clutch is difficult to engage.

Disclosure of Invention

The invention aims to overcome the defects that the prior tooth clutch which adopts spiral motion to realize tooth meshing forms limited tooth side clearance by thinning the tooth thickness and has lower meshing success probability (5-10 percent), and provides the tooth clutch with high meshing success probability, which can improve the meshing success probability of the clutch to more than 80 percent without reducing the bending and shearing strength of the torque transmission sleeve teeth.

The purpose of the invention is realized as follows: the sliding mechanism comprises an input assembly 100, a sliding assembly 200 and an output assembly 300, wherein the input assembly 100 is provided with an external spiral structure 110, the sliding assembly 200 is provided with a movable sleeve tooth 220 and an internal spiral mechanism 210, the output assembly 300 is provided with a static sleeve tooth 320, the external spiral structure is connected with the internal spiral mechanism, the static sleeve tooth is meshed with the movable sleeve tooth, one side of the end surface of the movable sleeve tooth, which is close to a non-torque transmission tooth surface, is provided with a section of inclined surface, one side of the end surface of the movable sleeve tooth, which is close to a torque transmission tooth surface, is provided with a straight surface, the inclined direction of the inclined surface of the end surface of; a section of inclined surface is formed on one side, close to the non-torque transmission tooth surface, of the end surface of the fixed sleeve tooth, a straight surface is reserved on one side, close to the torque transmission tooth surface, the inclined direction of the inclined surface of the end surface of the fixed sleeve tooth is the same as the moving direction of the movable sleeve tooth, and the inclined angle is beta.

The invention also includes such structural features:

1. the width of the straight surface of the movable sleeve tooth and the width of the inclined surface of the fixed sleeve tooth are both 5% of the tooth thickness, and the width of the inclined surface is 95% of the tooth thickness.

2. After the glide assembly alignment surface 205 is pressed against the input assembly alignment surface 120, torque is transferred through the input assembly to the output assembly through the glide assembly.

Compared with the prior art, the invention has the beneficial effects that: the invention ensures the bending and shearing strength of the torque transmission sleeve gear, improves the probability of successful meshing of the gear-type clutch which adopts the spiral motion to realize the meshing, improves the capacity of the clutch to adapt to the meshing with high speed difference, avoids the meshing and gear beating under the high speed difference and reduces the control difficulty of the clutch. A section of inclined surface is made at the end of each tooth of 2 pieces of mutually meshed torque transmission sleeve teeth, so that the tooth end surface of each tooth, which is originally vertical to the sleeve tooth axis, is changed into a special structure consisting of a plane and 2 sections of inclined surfaces. The bevel width is about 95% of the tooth thickness. In the process of meshing the clutch sleeve teeth, as long as the inclined planes of the tooth end surfaces are in contact with each other, the clutch sleeve teeth axially have meshing length, and can automatically complete all meshing under the action of spiral motion, because the width of the inclined planes is very large, the meshing success probability is greatly improved, the angle between the inclined planes and the tooth end surfaces is about 10-20 degrees, and the bending and shearing strength of the torque sleeve teeth are slightly influenced.

Drawings

Fig. 1 is a structural view of a dog clutch in which meshing of teeth is achieved by a screw motion (disengaged state).

Fig. 2 is a structural view of a dog clutch in which meshing of teeth is achieved using a screw motion (engaged state).

Fig. 3 is a schematic view of the movement of fig. 1 along the pitch circle of the torque sleeve teeth, which is developed into a plane.

Fig. 4-6 illustrate the process of the meshing movement of the set teeth with the flat end faces.

FIG. 7 is a schematic diagram of an improved probability of meshing using spaced tooth removal.

Fig. 8 is a configuration diagram (disengaged state) of the present invention.

Fig. 9 is a configuration diagram (engaged state) of the present invention.

Fig. 10 is a schematic diagram of the motion of the present invention.

Fig. 11-14 illustrate the engagement motion of the present invention.

FIG. 15 is an enlarged view of the moving set of teeth of the present invention.

Fig. 16 is an enlarged view of the fixed set of teeth of the present invention.

Fig. 17 is a partially enlarged view of fig. 9.

In each figure, 10 is input end rotation speed, 20 is output end rotation speed, 30 is tooth end surface clearance, 100 is input assembly, 110 is external spiral structure, 200 is sliding assembly, 210 is internal spiral mechanism, 220 is movable sleeve tooth, 230 is movable sleeve tooth groove width, 232 is movable sleeve tooth thickness, 234 is external acting force, 240 is connected, 250 is movable sleeve tooth end surface straight surface, 252 is movable sleeve tooth end surface inclined surface, 254 is movable sleeve tooth end surface inclined surface included angle, 256 is movable sleeve tooth non-torque tooth surface, 258 is movable sleeve tooth torque transmission tooth surface, 280 is burr generated by tooth beating, 290 is axial meshing length, 300 is output assembly, 320 is static sleeve tooth, 321 is static sleeve tooth separated from tooth, is static sleeve tooth groove width, 332 is static sleeve tooth thickness, 334 is residual plane width, 350 is static sleeve tooth end surface straight surface, 352 is static sleeve tooth end surface inclined surface, 354 is sleeve tooth end surface inclined surface, 356 is static sleeve tooth surface torque transmission tooth surface, 358. the non-torque transmission tooth surface of the static sleeve tooth.

Detailed Description

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

The invention relates to a tooth end structure for improving the meshing success probability of a tooth clutch, which is characterized in that inclined planes are arranged on the gear tooth end surfaces of movable sleeve teeth and static sleeve teeth of the tooth clutch which realizes tooth meshing by adopting spiral motion, and the tooth end structure is characterized in that: a section of inclined surface is formed on one side of the end surface of the movable sleeve tooth, which is close to the non-torque transmission tooth surface, a straight surface is reserved on one side of the end surface of the movable sleeve tooth, the width of the straight surface accounts for about 5% of the tooth thickness, the width of the inclined surface accounts for about 95% of the tooth thickness, the inclined direction of the inclined surface of the end surface of the movable sleeve tooth is opposite to the moving direction of the movable sleeve tooth, and the inclined angle is beta; one side of the end face of the static sleeve tooth, which is close to the non-torque transmission tooth face, is made into a section of inclined face, one side of the end face of the static sleeve tooth, which is close to the torque transmission tooth face, is kept into a straight face, the width of the straight face is about 5% of the tooth thickness, the width of the inclined face is about 95% of the tooth thickness, the inclined direction of the inclined face of the end face of the static sleeve tooth is the same as the moving direction of the movable sleeve. The tooth end face inclined plane of the movable sleeve tooth is positioned on the tooth end face of the tooth on the side where the movable sleeve tooth and the fixed sleeve tooth are meshed with each other. The tooth end face inclined plane of the static sleeve tooth is positioned on the tooth end face of the tooth on the side where the static sleeve tooth and the movable sleeve tooth are meshed. The inclined angles of the end face inclined planes of the moving sleeve teeth and the static sleeve teeth are equal. The widths of the end face inclined planes of the moving sleeve teeth and the static sleeve teeth are equal.

In fig. 1, the input assembly (100) is formed with an external helical structure (110), the glide assembly (200) is formed with a moving sleeve gear (220) and an internal helical mechanism (210), and the output assembly (300) is formed with a stationary sleeve gear (320). The outer helical structure is coupled to the inner helical mechanism such that the glide assembly can make a helical motion on the input assembly. The output assembly and the input assembly are coaxially arranged, and the static sleeve teeth and the dynamic sleeve teeth can be axially nested and meshed. In fig. 2, after the fixed sleeve teeth and the movable sleeve teeth are meshed and the positioning surface (205) of the sliding assembly is pressed with the positioning surface (120) of the input assembly, the torque can be transmitted to the output assembly through the sliding assembly.

In fig. 3-4, the distance between the end faces of the moving sleeve teeth and the fixed sleeve teeth is L1(30), the clutch is in a disengaged state, the input end rotating speed V1(10) is greater than the output end rotating speed V2(20), and V1-V2 is realized by controlling the rotating speed of equipment connected with the input end and the output end of the clutch, namely 5r/min to 10 r/min. An external force (234) is applied to the sliding assembly to enable the end face straight surface (250) of the moving sleeve gear to be in contact with the end face straight surface (350) of the fixed sleeve gear, the position relation of the moving sleeve gear and the fixed sleeve gear can be changed to the state shown in the figure 4 because V1 is larger than V2, and if V1-V2 are small in control and the speed of pushing the sliding assembly to move rightwards is fast enough, the moving sleeve gear and the fixed sleeve gear can be meshed axially. Assuming that S2 ═ S1 ═ 0.45 pi m, B2 ═ B1 ═ 0.55 pi m, probability of success of primary engagement: (B2-S1)/pi m (0.55-0.45)/2 0.05. As shown in FIG. 6, if V1-V2 is more than 5r/min to 10r/min, since the probability of success of one-time meshing is only 0.05, the tooth hitting phenomenon is very easy to occur, burrs (280) are generated, further the next meshing is influenced, the end faces of the gear teeth are easy to be seriously damaged after multiple times of tooth hitting, and the burrs falling from the tooth hitting are mixed into lubricating oil, so that the normal operation of other equipment is influenced.

As shown in fig. 7, with the scheme of removing the spaced teeth, the probability of success of one-time meshing is: (pi m + B2-S1)/2 pi m (1+0.55-0.45)/2 pi 0.55) has an increased probability of success in one-time engagement by 50%, but has the following disadvantages: the number of the transmission teeth is reduced by 50%, and the strength is reduced. If the strength is to be maintained, the pitch circle diameter of the torque transmission teeth must be increased, which results in a larger clutch volume.

In fig. 8, the input assembly (100) is formed with an external helical structure (110), the glide assembly (200) is formed with a moving sleeve gear (220) and an internal helical mechanism (210), and the output assembly (300) is formed with a stationary sleeve gear (320). The outer helical structure is coupled to the inner helical mechanism such that the glide assembly can make a helical motion on the input assembly. The output assembly and the input assembly are coaxially arranged, and the static sleeve teeth and the dynamic sleeve teeth can be axially nested and meshed. The end face of the movable sleeve tooth (220) is provided with a movable sleeve tooth end face inclined plane (252), the end face of the static sleeve tooth (320) is provided with a static sleeve tooth end face inclined plane (352), and the included angles between the movable sleeve tooth end face inclined plane (252) and the static sleeve tooth end face inclined plane (352) and the respective tooth end faces are the same and can be matched with each other when in contact.

In fig. 9, after the fixed sleeve teeth and the moving sleeve teeth are meshed and the positioning surface (205) of the sliding assembly is pressed with the positioning surface (120) of the input assembly, the torque can be transmitted to the output assembly through the sliding assembly.

The clutch shown in fig. 10 is in a disengaged state, the distance between the end faces of the moving sleeve teeth and the fixed sleeve teeth is L1(30), the input end rotating speed V1(10) is greater than the output end rotating speed V2(20), and V1-V2-5 r/min-10 r/min are achieved by controlling the rotating speed of equipment connected with the input end and the output end of the clutch. In fig. 11, an external force (234) is applied to the sliding assembly, so that the end face inclined surface (252) of the movable sleeve tooth is in contact with the end face inclined surface (352) of the fixed sleeve tooth, and since V1 is larger than V2, the end face inclined surface (252) of the movable sleeve tooth is always pressed on the end face inclined surface (352) of the fixed sleeve tooth under the action of the external force (234) in the rotating process, so that the movable sleeve tooth is inevitably axially displaced in the rotating process.

As shown in fig. 12, even if V1-V2>5r/min to 10r/min and the speed of F pushing the sliding component to move rightwards is small, the position relationship between the moving set teeth and the fixed set teeth will be turned to the state of fig. 13, at this time, the fixed set teeth and the moving set teeth have generated axial meshing without generating tooth-beating burrs, the meshing length is L (290), and L is (S2-S3) tan (beta). As the input assembly continues to rotate, the moving and stationary sleeve teeth continue to axially mesh until the glide assembly locating surface (205) compresses the input assembly locating surface (120).

As shown in fig. 11, assume that S2 ═ S1 ═ 0.45 pi m, B2 ═ B1 ═ 0.55 pi m, and S3 ═ 0.05 pi m (334) one-time meshing success probability: (pi m-2S 3)/pi m ═ 1-2 × 0.05)/1 ═ 0.90. The probability of one-time meshing success is far greater than that of a meshing scheme 0.55 adopting the removed spacing teeth. Because the end face inclined plane (252) of the moving sleeve tooth and the end face inclined plane (352) of the fixed sleeve tooth do not influence the contact length of the meshing of the moving sleeve tooth torque transmission tooth face (258) and the fixed sleeve tooth torque transmission tooth face (356), the shearing strength and the bending strength of the tooth are not changed.

In fig. 15, on the gear tooth end face (250) on the side where the movable sleeve gear and the fixed sleeve gear are engaged with each other, a section of inclined surface (252) is formed on the side close to the non-torque-transmitting gear surface (256), a straight surface is reserved on the side close to the torque-transmitting gear surface (258), the width S3 of the straight surface (334) accounts for about 5% of the tooth thickness S1(232), and the width of the inclined surface accounts for about 95% of the tooth thickness S1 (232). The inclined direction of the end face inclined plane of the movable sleeve gear is opposite to the moving direction of the movable sleeve gear, the movable sleeve gear moves rightwards in fig. 15, the inclined plane inclines leftwards, and the inclined angle is beta

In fig. 16, a bevel (252) is formed on the end face (350) of the tooth on the side where the fixed sleeve tooth and the movable sleeve tooth are engaged with each other, on the side close to the non-torque-transmitting tooth face (358), and a straight face is left on the side close to the torque-transmitting tooth face (356), the width S3 of the straight face (334) accounts for about 5% of the tooth thickness S1(232), and the width of the bevel accounts for about 95% of the tooth thickness S2 (332). The inclined direction of the end face inclined plane of the static sleeve tooth is the same as the moving direction of the movable sleeve tooth, the movable sleeve tooth moves rightwards in the figure 15, the end face inclined plane of the static sleeve tooth inclines rightwards, the inclined angle is beta, and the inclined angles of the end face inclined planes of the movable sleeve tooth and the static sleeve tooth are equal.

For the gear clutch which adopts the spiral motion to realize the meshing of the gear, the gear end part structure of the invention can greatly improve the probability of one-time meshing success, thereby being very easy to avoid the meshing gear beating phenomenon under high rotating speed difference and reducing the control difficulty of the rotating speed of equipment at two ends of the clutch when the clutch is meshed.

In summary, the present invention provides a tooth end structure for improving the probability of successful engagement of a tooth clutch. A section of inclined plane is formed on the end face of the gear teeth of the movable sleeve gear and the fixed sleeve gear, wherein the side close to the non-torque transmission gear surface is provided with a straight surface, and the width of the inclined plane accounts for about 95% of the thickness of the gear. The inclined direction of the end face inclined plane of the movable sleeve tooth is opposite to the moving direction of the movable sleeve tooth, the inclined direction of the end face inclined plane of the static sleeve tooth is the same as the moving direction of the movable sleeve tooth, and the inclined angles of the end face inclined planes of the movable sleeve tooth and the static sleeve tooth are equal. When meshing, the movable sleeve gear moves towards the static sleeve gear under the action of external force, the end face inclined planes of the movable sleeve gear and the static sleeve gear are in mutual contact, along with the rotation of the movable sleeve gear, the movable sleeve gear generates an axial movement distance L relative to the static sleeve gear due to the action of the inclined planes, when the gear tooth of the movable sleeve gear rotates over the current static sleeve gear tooth in contact with the movable sleeve gear and is in contact with the working tooth face of the next static sleeve gear tooth, the distance L can avoid the gear beating phenomenon, the probability of one-time meshing success of the sleeve gear is improved, and the sleeve gear keeps the torque transmission strength from being reduced.