JP2009108878A - Engaging clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an engaging clutch capable of reducing gear shifting time with a simple structure. <P>SOLUTION: In a spline clutch, spline teeth of male spline 8a or 8b are inserted in a sleeve (female spline) 7a and both of the male and the female splines 7a, and 8a or 8b are fitted. Spline teeth per predetermined number of spline teeth of the male spline 8a or 8b and the female spline 7a are projected to an insertion side surface side in axial direction to form fitting guide teeth. Since fitting guide teeth of both of the splines 7a, 8b mutually abut by moving the female spline 7a to the male spring 8b, both splines 7a, 8b get in a synchronized state. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a spline-coupled meshing clutch suitable for use in a transmission having a large transmission torque, such as an automobile or a large special work vehicle.

  In general, the meshing clutch is called a dog clutch or a pawl clutch, and once it is coupled, power such as hydraulic pressure is not required to maintain the coupled state, so that input torque can be transmitted to the output side without loss. For these reasons, it is used in manual transmissions and automated manual transmissions called robotized manuals.

  As is well known, the meshing clutch includes a spline clutch and a dog clutch. The spline clutch engages the spline teeth of the male and female splines by fitting the spline teeth of the male spline into the spline groove of the female spline. The dog clutch is a gear and sleeve (movable in the axial direction on the rotating shaft). A plurality of dog teeth (protruding teeth) are provided in the circumferential direction on the opposite side surfaces of each other, and the dog teeth mesh with each other to transmit torque.

  A spline clutch is well known without mentioning a publicly known example, and a dog clutch is described in, for example, Patent Document 1 below. Patent Document 1 also describes that the length of the dog teeth provided on the gear and the sleeve is increased every other dog tooth so that the dog teeth can be easily bitten and the gears are quickly shifted.

  However, the dog clutch has a limit in the shear stress that is handled by the dog teeth, and in order to increase the transmission torque capacity, there is a problem that the diameter must be increased and the size is increased. For this reason, many spline clutches are used in transmissions having a large transmission torque capacity.

  By the way, the spline clutch engages and connects the spline teeth of both splines to the spline groove of the other spline while both the male and female splines are rotating. For example, in a manual transmission, while the power from the engine is cut off by a friction clutch, the meshing clutch of the front gear is released and the meshing clutch of the next gear is coupled.

  The coupling of both male and female splines must be in a state where the rotational speed and phase of both splines are equal, that is, in a synchronized state. For this reason, a brake device is provided on a shaft (for example, a countershaft) that freely rotates when the engine is disconnected, or a friction ring called a synchronizer is provided on the meshing clutch for mechanical synchronization. In addition, the engine speed is controlled and synchronized.

JP 2007-120723 A

  The conventional technology synchronizes with the friction force of the countershaft brake and the synchromesh mechanism, or synchronizes by controlling the engine speed, which makes the configuration complicated and also increases the shift time. Have In addition, there is a practical problem that maintenance is required because of wear when synchronized by frictional force.

  An object of the present invention is to provide a meshing clutch capable of shortening a shift time with a simple configuration.

  A feature of the present invention is a spline clutch in which a male spline and a female spline are inserted into a spline groove of a female spline so that both male and female splines are fitted. The male spline and the female spline have a predetermined number of spline teeth. There exists in the fitting guide tooth which protruded each spline tooth to the insertion side surface side to the axial direction.

  In other words, according to the present invention, a predetermined number of spline teeth in both male and female cylindrical splines protrude in the axial direction toward the insertion side surface and are longer than the other spline teeth, and the axial direction of the predetermined number of spline teeth A fitting guide tooth is formed by a portion protruding in the direction.

  In the present invention, both male and female splines are formed with fitting guide teeth that protrude in the axial direction toward the side of the side where the spline teeth are inserted into a predetermined number of spline teeth. Since the fitting guide teeth of both splines come into contact with each other due to the relative speed difference, both splines can be synchronized in a short time. Therefore, since the spline teeth of both splines can be quickly fitted into the spline grooves of the other spline, the shift time can be shortened with a simple configuration.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  A first embodiment of the present invention will be described with reference to FIGS.

  FIG. 1 is a configuration diagram of a twin clutch type automatic transmission which is an example in which the present invention is used. In FIG. 1, the output shaft of the engine 1 is connected to the input shaft 3 of the transmission 2. Two friction clutches 4 a and 4 b can be coupled to the input shaft 3. The friction clutch 4a is connected to an odd intermediate shaft (rotary shaft) 5a having an odd-numbered transmission gear train, and the friction clutch 4b is connected to an even intermediate shaft (rotating shaft) 5b having an even-numbered transmission gear train.

  A first gear 6a, a third gear 6b, a fifth gear 6c, and a reverse gear 6d are rotatably installed on the odd intermediate shaft 5a. A second speed gear 6e and a fourth speed gear 6f are rotatably installed on the even intermediate shaft 5b. The transmission gears 6 a to 6 f at each stage are meshed with the corresponding transmission output gears 10 a to 10 f, and the transmission output gears 10 a to 10 f are fixed to the output shaft 11.

  The odd intermediate shaft 5a is provided with a spline clutch, which is a meshing clutch of the present invention, for switching between the first speed gear 6a and the third speed gear 6b. A male spline 9a is fixed to the odd intermediate shaft 5a. The female spline sleeve 7a meshes with the male spline 9a fixed to the odd intermediate shaft 5a, and is installed so as to be movable in the axial direction of the odd intermediate shaft 5a.

  The first-speed gear 6a is provided with a male first-line gear spline 8a that meshes with the sleeve 7a. Similarly, the third speed gear 6b is provided with a male spline third speed gear spline 8b that meshes with the sleeve 7a. The male splines 8a and 8b are provided coaxially with the rotary shaft 5a so as to be relatively rotatable. When a thrust is applied by a shift fork (not shown), the sleeve 7a moves in the left-right axial direction of the rotary shaft 5a and meshes with the male spline 8a of the first gear 6a or the male spline 8b of the third gear 6b, thereby changing the gear stage. Can be switched.

  The spline clutch includes a rotating shaft 5a, a male spline 9a, a sleeve (female spline) 7a, a male spline 8a, and a male spline 8b.

  The odd-numbered intermediate shaft 5a is further provided with a spline clutch of the present invention for switching between the fifth speed gear 6c and the reverse gear 6d. The male spline 8d is provided.

  The even-numbered intermediate shaft 5b is provided with a spline clutch of the present invention for switching between the second speed gear 6e and the fourth speed gear 6f. The male spline 9c, the sleeve 7c, the male spline 8e of the second speed gear 6e, the fourth speed. A male spline 8f of the gear 6f is provided.

  FIG. 2 is an enlarged view of a spline clutch that switches between the first speed gear 6a and the third speed gear 6b of FIG. A spline clutch that switches between the fifth gear 6c and the reverse gear 6d and a spline clutch that switches between the second gear 6e and the fourth gear 6f are configured similarly.

  3 and 4 are exploded views showing the male splines 8a, 8b and 9a and the female spline 7a of FIG. 3A shows the male splines 8a, 8b, and 9a, and FIG. 3B is a left side view of the male spline 8b. 4A shows the female spline 7a, and FIG. 4B is a right side view of the female spline 7a.

  As shown in the perspective view of FIG. 5, the male spline 8b is formed in a cylindrical shape, and a plurality of spline teeth 81 and spline grooves 82 are formed on the outer peripheral surface. Spline shows an example of an involute spline. The male spline 8b is formed such that a predetermined number of spline teeth 81 project from the side of the side surface 84 into which the sleeve (female spline) 7a is fitted.

  The protruding portion of the spline tooth 81 protrudes in the axial direction of the cylindrical male spline 8 b and forms a fitting guide tooth 83. In other words, the cylindrical male spline 8b is formed longer than the other spline teeth 81 with a predetermined number of spline teeth 81 protruding in the axial direction toward the side of the insertion side.

  FIG. 5 shows an example in which fitting guide teeth 83 are formed on every two spline teeth 81. The length of the fitting guide teeth 83 is about 2 mm. In FIG. 3B, the fitting guide teeth 83 are marked with a number of marks for easy identification.

  On the other hand, as shown in the perspective view of FIG. 6, the sleeve (female spline) 7a is formed in a cylindrical shape, and a plurality of spline teeth 71 and spline grooves 72 are integrally formed on the inner peripheral surface. The spline of the female spline 7a is also an involute spline. The female spline 7a is formed such that a predetermined number of spline teeth 71 of the spline teeth 71 protrude to the side of the insertion side surface 74 with the male spline 8b.

  The protruding portion of the spline teeth 71 protrudes in the axial direction of the cylindrical female spline 7 a to form a fitting guide tooth 73. In other words, the cylindrical female spline 7 a is formed longer than the other spline teeth 71 with a predetermined number of spline teeth 71 protruding in the axial direction toward the side of the insertion side.

  FIG. 6 shows an example in which fitting guide teeth 73 are formed on every two spline teeth 71. The length of the fitting guide teeth 73 is about 2 mm which is the same as the fitting guide teeth 83 of the male spline 8b. In FIG. 4B, a large number of marks are attached to the fitting guide teeth 73 for easy identification.

  The insertion side surface side of the male spline 8b and the sleeve 7a with the male spline 8b is configured in this way, but the side surface side of the male spline 8a and the sleeve 7a with the male spline 8a is also configured in the same manner. The other sleeves 7b and 7c and the male splines 8c to 8f are configured similarly to the sleeve 7a or the male spline 8b.

  The spline clutch of the present invention is configured as described above. Next, the behavior in which the male spline 8b and the female spline 7a are fitted and connected will be described with reference to FIGS. 7 to 10 schematically show the spline teeth and the spline grooves in a straight line. Moreover, the figure (a) of FIGS. 7-10 is the top view seen from the groove surface, and the figure (b) is the side view which looked at figure (a) from the side. Further, it is assumed that the male spline 8b and the female spline 7a are rotationally moved upward in the drawing, and the rotational speed of the male spline 8b is somewhat high.

  FIG. 7 shows a case in which the male spline 8b and the female spline 7a are most difficult to be coupled. In this state, the tip surfaces of the joint guide teeth 73 are in contact with each other. In addition, capital letters A, B, and C are attached to the fitting guide teeth 73 of the female spline 7a so that the time series position transition state of the fitting guide teeth 73 of the female spline 7a and the fitting guide teeth 83 of the male spline 8b can be understood. The fitting guide teeth 83 of the male spline 8b are shown with small letters a, b, and c.

  If the male spline 8b rotates faster in this state, the fitting guide tooth 73A slides down from the fitting guide tooth 83a, and the fitting guide tooth 73B slides down from the fitting guide tooth 83b. At this time, there are cases where the male spline 8b and the female spline 7a can be synchronously coupled as soon as they slide down. However, if the relative speed difference between the male spline 8b and the female spline 7a is large, most of the fitting guide teeth 73B and 73C are in contact with the spline teeth 81 of the male spline 8b as shown in FIG. The guide teeth 83a and 83b are in contact with the spline teeth 71 of the female spline 7a.

  When the phase shifts from the state of FIG. 8, when the relative speed difference is small, the spline teeth 81 of the male spline 8b may be inserted into and inserted into the spline groove 72 of the female spline 7a, and may be coupled synchronously. However, if the relative speed difference is large, the spline teeth 81 of the male spline 8b pass through the spline groove 72 of the female spline 7a and cannot be synchronously coupled.

  The phase shifts from the state of FIG. 8 to the state shown in FIG. In FIG. 9, the fitting guide teeth 83a abut on the fitting guide teeth 73B, and the fitting guide teeth 83b abut on the fitting guide teeth 73C. Therefore, the male spline 8b and the female spline 7a are in a synchronized state. Since the female spline 7a is thrust in the axial direction of the rotary shaft 5a, the spline teeth 81 of the male spline 8b and the spline teeth 71 of the female spline 7a are inserted into the spline grooves 72 and 82 of the counterpart splines 7a and 8b. .

  The spline teeth 81 of the male spline 8b and the spline teeth 71 of the female spline 7a are fitted and inserted up to the meshing depth L as shown in FIG. In this state, the mesh fitting of the spline teeth 81 of the male spline 8b and the spline teeth 71 of the female spline 7a is completed, and the switching of the spline clutch is completed.

  As described above, in the meshing clutch of the present invention, both male and female splines are formed with fitting guide teeth that protrude in the axial direction toward the insertion side surface on the spline teeth for each predetermined number of spline teeth. When a thrust is applied to one of the splines and moved, the fitting guide teeth of both splines abut and engage with each other, so that both splines can be synchronized in a short time. Accordingly, the spline teeth of both male and female splines can be quickly fitted into the spline grooves of the counterpart spline so that both male and female splines can be fitted, and the shift time can be shortened with a simple configuration.

  Further, since there is no synchronization using frictional force, there is a practical effect that it is not necessary to perform maintenance due to wear of parts.

  In the first embodiment, the female spline is moved in the direction of the rotation axis. However, the same effect can be obtained by forming the spline to be moved in the male spline and forming the other spline in the female spline. Of course.

  In the first embodiment, an example of an involute spline is described. However, it is obvious that a spline having another cross-sectional shape such as a trapezoidal spline or a square spline may be used.

  In Example 1, both male and female splines are provided with fitting guide teeth on every two spline teeth. However, any number of splines may be provided by evenly allocating them so as to achieve rotational balance. It is also possible to vary the number of spline teeth on which the fitting guide teeth are provided for the female spline.

  FIG. 11 shows an example of the second embodiment. In FIG. 11, the spline teeth provided with the fitting guide teeth in the male spline 8 are marked with ○, and the spline teeth provided with the fitting guide teeth in the female spline 7 are marked with ●.

  FIG. 11A shows an example in which fitting guide teeth are provided on every other spline teeth of both male and female splines 7 and 8, and FIG. 11B shows five pieces of both male and female splines 7 and 8. This is an example in which fitting guide teeth are provided on the stationary spline teeth. FIG. 11C is an example in which the male spline 8 is provided with fitting guide teeth on every fifth spline teeth, and the female spline 7 is provided with fitting guide teeth on every second spline teeth. 11 (d) is an example in which the male spline 8 is provided with fitting guide teeth on every eleven spline teeth, and the female spline 7 is provided with fitting guide teeth on every fifth spline teeth.

  If the number of spline teeth provided with fitting guide teeth is reduced as shown in FIGS. 11B, 11C, and 11D, the chances of biting increase, but the time until the synchronization state is reached. It is slightly longer than the example of FIG. Further, when the fitting guide teeth of both male and female splines 7 and 8 are engaged and synchronized with each other, the impact per tooth increases when they are hit with a small number of fitting guide teeth, but the moment of inertia of the spline shaft, etc. It will be designed in consideration of.

  In the second embodiment, as in the first embodiment, both male and female splines are formed with fitting guide teeth protruding in the axial direction toward the insertion side surface of the spline teeth for each predetermined number of spline teeth. When the spline is moved by applying a thrust, the fitting guide teeth of both splines are brought into contact with each other, so that both splines can be synchronized in a short time. Therefore, the spline teeth of both splines can be quickly inserted into the spline grooves of the counterpart spline so that both male and female splines can be fitted, and the shift time can be shortened with a simple configuration.

It is a block diagram which shows an example of the automatic transmission in which this invention is used. It is the elements on larger scale of the spline clutch of FIG. 1 which shows 1st Example of this invention. FIG. 3 is an exploded view showing the male spline of FIG. 2 in an exploded manner. It is the exploded view which decomposed | disassembled and showed the female spline of FIG. It is an expansion perspective view of the male spline of FIG. It is an expansion perspective view of the sleeve (female spline) of FIG. It is operation | movement explanatory drawing of 1st Example of this invention. It is operation | movement explanatory drawing of 1st Example of this invention. It is operation | movement explanatory drawing of 1st Example of this invention. It is operation | movement explanatory drawing of 1st Example of this invention. It is a block diagram which shows 2nd Example of this invention.

Explanation of symbols

  1: engine, 2: transmission, 3: input shaft, 4a, 4b: friction clutch, 5a, 5b: intermediate shaft (rotary shaft), 6a-6f: transmission gear, 7a-7c: sleeve (female spline), 8a 8f: male spline, 9a-9c: shaft fixed male spline, 10a-10f: speed change output gear, 11: output shaft, 71: female spline teeth, 72: female spline groove, 73, 83: fitting guide teeth, 81 : Male spline tooth, 82: Male spline groove.

Claims (3)

  A cylindrical male spline having a plurality of spline teeth and spline grooves formed on the outer peripheral surface, and a cylindrical female spline having a plurality of spline teeth and spline grooves formed on the inner peripheral surface, A meshing clutch that engages both splines by applying thrust to one spline while both female splines are rotating, wherein the male spline and the female spline are provided with a predetermined number of spline teeth. A meshing clutch characterized in that fitting guide teeth protruding in the axial direction toward the fitting side surface are formed.   A cylindrical male spline that is provided coaxially with the rotating shaft so as to be relatively rotatable and has a plurality of spline teeth and spline grooves formed on the outer peripheral surface, and is mounted and fixed to the rotating shaft so as to be movable in the axial direction. A cylindrical sleeve having a plurality of spline teeth and spline grooves formed on an inner peripheral surface, and the male spline is moved in the axial direction while the male spline and the sleeve are rotating. The male spline and the sleeve are formed with fitting guide teeth each having a predetermined number of spline teeth protruding in the axial direction toward the insertion side surface. An engagement clutch, wherein the fitting guide teeth of the spline and the sleeve are brought into contact with each other to bring the male spline and the sleeve into a synchronized state.   The mesh clutch according to any one of claims 1 and 2, wherein both the male and female splines or the number of spline teeth on which the fitting guide teeth of the male spline and the sleeve are formed are different.

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