阅读说明：本技术 用于车辆变速器的同步组件的托板 (Carrier for a synchronizing assembly of a vehicle transmission ) 是由 丹尼尔·克鲁格 托马斯·莫德洛克 帕特里克·费舍尔 于 2020-04-10 设计创作，主要内容包括：本发明涉及用于车辆变速器的同步组件的托板(30),该托板具有基体(40)、设置在基体(40)中的弹簧(36)以及卡锁元件(34),该卡锁元件被弹簧(36)压靠到基体(40)中的止挡(46)上,其特征在于,卡锁元件(34)具有凸状的卡锁面(35)以及与该卡锁面对置的用于弹簧(36)的削平的贴靠面(50)。(The invention relates to a carrier (30) for a synchronizing assembly of a vehicle transmission, comprising a base body (40), a spring (36) arranged in the base body (40), and a latching element (34) which is pressed by the spring (36) against a stop (46) in the base body (40), characterized in that the latching element (34) has a convex latching surface (35) and a flattened contact surface (50) opposite the latching surface for the spring (36).)

1. Carrier (30) for a synchronizing assembly of a vehicle transmission, comprising a base body (40), a spring (36) arranged in the base body (40), and a latching element (34) which is pressed against a stop (46) in the base body (40) by the spring (36), characterized in that the latching element (34) comprises a convex latching surface (35) and a flattened contact surface (50) opposite the latching surface for the spring (36).

2. The pallet (30) of claim 1, wherein the abutment surface (50) is annular.

3. A pallet (30) according to claim 1 or 2, characterized in that a centering protrusion (52) is provided inside the abutment surface (50), which centering protrusion extends into the spring (36).

4. A pallet (30) according to any one of the preceding claims, characterized in that the base body (40) has a spring receptacle (42) closed in the axial direction of the spring (36), which spring receptacle has a bottom (44).

5. A pallet (30) according to any one of the preceding claims, characterized in that the abutment surface (50) is located at the height of the centre of curvature of the detent surface (35) seen in cross-section.

6. A pallet (30) according to any one of the preceding claims, characterized in that the centring projection (52) has a length at least equal to the radius of the detent face (35).

7. A pallet (30) according to claim 6, characterized in that the centring projection (52) has a length which is larger than the radius of the detent face (35), in particular in the order of magnitude of the diameter of the detent face (35).

8. A pallet (30) according to any one of the preceding claims, characterized in that the centring projection (52) is provided with a lead-in chamfer (53).

9. A pallet according to any one of the preceding claims, characterized in that a lead-in chamfer (60) is provided at the transition from the abutment surface (50) to the latching surface (35).

10. A pallet according to claim 9, characterized in that the lead-in chamfer (60) is a conical chamfer.

11. A pallet according to claim 9, characterized in that the lead-in chamfer (60) has an outer contour which is curved in cross-section.

12. A pallet according to any one of claims 9-11, characterized in that a circumferential support surface (62) on the detent element (34) is provided between the lead-in chamfer (60) and the detent surface (35), which support surface interacts with the base body.

13. A pallet according to claim 12, characterized in that the support surface (62) extends substantially parallel to the centre axis of the snap-lock element (34).

14. A pallet (30) as claimed in claim 13, characterized in that the supporting surface (62) is cylindrical.

Technical Field

The invention relates to a carrier plate for a synchronizing assembly of a vehicle transmission, comprising a base body, a spring arranged in the base body, and a latching element which is pressed against a stop in the base body by the spring.

Background

The synchronizing assembly has a hub, at least one carrier plate and at least one synchronizing ring. The synchronization assembly is used to couple a transmission gear to a transmission shaft carrying the gear when the respective gear is to be engaged.

Such synchronization assemblies are well known in a variety of different designs. The hub is usually mounted on the shaft of the manual transmission in a rotationally fixed manner. A sliding sleeve is arranged on the hub in a rotationally fixed but axially displaceable manner, which sliding sleeve serves to establish a desired rotationally fixed connection to one transmission gear (or to a plurality of transmission gears if transmission gears are arranged on both sides of the hub). In order to be able to establish a rotationally fixed connection, the transmission gear is provided with a shifting tooth, onto which the edge section of the sliding sleeve can be pushed.

Before the sliding sleeves engage in the shifting teeth of the respective gear wheels, the rotational speed of the hub must be synchronized on the one hand with the sliding sleeves and on the other hand with the transmission gear wheels. For this purpose, at least one synchronizing ring is provided, which is arranged on the hub and engages with corresponding friction surfaces assigned to the transmission gear wheels as soon as the sliding sleeve is moved out of its center position or neutral position. As long as there is a relative rotational speed between the hub and the transmission gear, the synchronizer ring is loaded in the circumferential direction relative to the hub into a locking position in which the sliding sleeve cannot engage into the shifting teeth of the transmission gear. Only when the rotational speeds are completely (or at least almost completely) equal and therefore no (or only a small) drag torque acts on the synchronizer ring can the synchronizer ring be twisted relative to the hub, so that the sliding sleeve can be shifted. This manner of functioning is well known. It is also known to provide a plurality of support plates in the hub, which serve to center the sliding sleeve in its central position and to engage the respective synchronizing ring with the friction surfaces assigned to it at the beginning of a shifting operation.

The carrier plate is usually fitted in a recess of the hub, wherein the latching elements are spring-loaded outward in the radial direction into latching recesses on the inside of the shift sleeve. At the beginning of the shifting operation, the carrier plate is initially moved in the axial direction, as a result of which a force is exerted on the respective synchronizer ring. This force is used to create the desired friction torque. When the shifting sleeve can be shifted after the rotational speed of the transmission shaft and the rotational speed of the gear wheel are synchronized in order to establish a rotationally fixed connection between the transmission shaft and the gear wheel, the detent elements are pressed in the radial direction into the carrier plate against the action of the spring, so that the detent elements do not hinder the shifting.

Balls are often used as detent elements. The ball is located on the end face of the spring, wherein the spring has a sufficient length to enable the engagement element to be recessed into the base body when the shifting sleeve is shifted.

The length of the spring cannot be less than a certain minimum length, in view of the fatigue strength of the spring and the required travel of the catch element during shifting. However, for certain designs (in particular for transmission shafts with a very large diameter), it is desirable to design the radial design height of the carrier plate to be particularly small.

Disclosure of Invention

The object of the invention is therefore to improve a pallet of the type mentioned at the outset such that it has a particularly small height.

In order to achieve the object, according to the invention: the locking element has a convex locking surface and a flattened contact surface for the spring opposite the locking surface. The invention is based on the following recognition: the detent element does not necessarily have to be spherical and the overall height in the radial direction can be reduced by a shape other than spherical.

According to one embodiment of the invention, the following are provided: the abutment surface is annular. The contact surface thus corresponds to the end face of the spring, which presses the latching element against a stop in the base body.

Preferably, a centering projection is provided on the inside of the contact surface, which centering projection extends into the spring. This prevents the detent element from twisting so far that the spring can be deflected as a result of the force exerted on it by the sliding sleeve sliding on it.

According to one embodiment of the invention, the following are provided: the base body has a spring receptacle closed in the axial direction of the spring, which has a bottom. Due to the small overall height of the carrier plate in the radial direction with respect to the hub, it is possible to design the spring receptacle to be closed, so that the carrier plate can be installed in the hub as a preassembled component at low cost.

According to one embodiment of the invention, the following are provided: viewed in cross section, the contact surface of the latching element is located at the level of the center of curvature of the latching surface. According to this embodiment, the "upper" half of the spherical surface remains on the detent element, so that this surface is used without functional change for interacting with stops in the shifting sleeve and the base body. However, the desired small structural height is achieved.

The centering projection may have a length corresponding to a radius of the detent surface. This has proven to be a good compromise between small size and good centering. In addition, it is possible for the centering projections to be produced from the material of the entire ball.

In principle, the centering projection should have a length which ensures that the guide in the spring does not tilt. However, the length is not allowed to be so large that the centering projection collides with the spring bottom in the maximum compression state. The minimum length of the centering projection should correspond at least to the height of the detent surface.

According to an alternative embodiment, the centering projection can have a length which is greater than half the diameter of the head of the latching element. In particular larger than the diameter of the head of the latching element. Improved centering is thereby obtained.

According to one embodiment: the centering protrusion is provided with a lead-in slope, thereby improving assemblability.

In order to keep the machining costs low, the detent elements are produced from rivets having a hemispherical head, which are hardened in the desired manner.

In order to facilitate the assembly of the latching element into the base body, a lead-in chamfer can also be provided at the transition from the contact surface to the latching surface.

According to one embodiment, the insertion bevel can be designed as a conical chamfer. It is also possible for the lead-in chamfer to have an outer contour which is curved at will in cross section.

In order to be able to better guide the lateral forces exerted by the sliding sleeve on the detent element during a gear change into the carrier plate, according to one embodiment a circumferential support surface is provided on the detent element between the lead-in ramp and the detent surface, which support surface interacts with the base body. The support surface significantly reduces the surface pressure and therefore also the wear between the latching element and the base body, so that a significantly longer service life and a constantly maintained force characteristic are achieved.

The support surface can extend substantially parallel to the center axis of the latching element, so that no axial forces are generated when the support surface is pressed against the base body. In addition, a greatly reduced surface pressure is achieved.

The support surface can be cylindrical in particular, i.e. have a certain extent parallel to the center axis of the latching element, so that a contact is produced between the base body and the latching element over a larger surface.

Drawings

The invention is described below with the aid of embodiments shown in the drawings. In the drawings:

FIG. 1 shows a cross-sectional view of a synchronizing assembly according to the prior art;

FIG. 2 shows an enlarged view of section II of FIG. 1;

fig. 3 shows an example of a pallet known from the prior art on a further enlarged scale;

FIG. 4 shows a sectional view of the support plate according to the invention and a view of the base body of the support plate without the spring and the catch element in a view corresponding to FIG. 3;

FIG. 5 shows a side view of the pallet of FIG. 4;

FIG. 6 shows a side view of a latch element for a pallet according to a second embodiment;

FIG. 7 shows a side view of a latch element for a pallet according to a third embodiment;

FIG. 8 shows a side view of a latch element for a pallet according to a fourth embodiment;

fig. 9 shows a side view of a latching element for a carrier according to a fifth embodiment.

Detailed Description

In the drawing, a synchronizing assembly 5 is shown, which serves to connect two transmission gears 7, 9, which are shown schematically here, in a rotationally fixed manner to a transmission shaft (not shown). For simplicity, the transmission gears 7, 9 are shown here with the same diameter; in fact, they have different diameters. It is of course also possible for the synchronization module to be equipped with only one gear and therefore only one transmission gear.

The synchronizing assembly 5 comprises a hub 10 (also referred to as synchronizer body) which is arranged on the transmission shaft in a rotationally fixed manner by means of a hub toothing 12. The transmission shaft extends along a central axis M, which is at the same time the central axis and the axis of rotation for the transmission gears 7, 9 and the synchronizing assembly 5.

The transmission gears 7, 9 are arranged as loose wheels on the transmission shaft. When one of the gears is to be used, which is assigned the respective transmission gear 7, 9, this transmission gear must be connected to the transmission shaft in a rotationally fixed manner. This is achieved here by means of a bog warner synchronization system, which is known per se and only the essential features of which are explained below.

The hub 10 is provided along its outer circumference with a sliding sleeve toothing 14, on which a sliding sleeve 16 is arranged non-rotatably, but movably in the axial direction. For this purpose, an internal toothing 17 is provided on the inner circumference of the sliding sleeve 16. A shift fork (not shown) can co-act with the sliding sleeve 16 to change gears.

Each transmission gear wheel 7, 9 is provided with a shift tooth 18, onto which the sliding sleeve 16 can be pushed with its inner tooth 17 in such a way that it slides correspondingly far in the axial direction from the central or neutral position shown in the figures. This results in a rotationally fixed connection from the transmission shaft via the hub 10 and the sliding sleeve 16 to the respective transmission gear 7 or 9, so that the respective gear can be used for torque transmission.

In view of wear and comfort, a rotationally fixed connection between the sliding sleeve 16 and the respective shifting tooth 18 can be established in a meaningful manner only if the rotational speed of the sliding sleeve 16 and the rotational speed of the respective gear wheel 7 or 9 are identical or at least approximately identical. To ensure this, the rotational speeds of the individual components are synchronized at the beginning of the shifting process.

For this purpose, at least one synchronizer ring 20 is provided for each transmission gear, the main tasks of which are: as soon as the sliding sleeve 16 moves out of its central position toward the transmission gear 7 or 9, it engages frictionally with a friction surface assigned to the respective transmission gear 7 or 9. The corresponding synchronizer ring 20 also has the function of: as long as the rotational speeds of the hub 10 and thus of the sliding sleeve 16 on the one hand and of the respective transmission gear 7 or 9 on the other hand are not yet sufficiently equal to one another, shifting of the sliding sleeve, i.e. engagement into the shifting tooth 18, is prevented. For this purpose, each synchronizer ring 20 has a locking toothing 22 with a tooth module corresponding to the tooth modules of the sliding sleeve toothing 14 and of the internal toothing 17 of the sliding sleeve 16.

Each synchronizer ring 20 is mounted to the hub 10 such that it can be twisted in a limited manner in the circumferential direction. The possible angle of rotation is set here such that the teeth of the locking toothing 22 of the synchronizer ring 20 lie opposite the teeth of the inner toothing of the sliding sleeve 16 when the synchronizer ring is in the maximum rotation position. Only when the rotational speeds of the sliding sleeve 16 and the respective transmission gear 7, 9 are at least almost equal and thus no or at least almost no drag torque acts on the synchronizer ring 20 can this synchronizer ring be rotated axially back into a position in which the sliding sleeve 16 can be adjusted in the axial direction until it engages in the shifting tooth 18 of the respective transmission gear or 9, by the interaction of suitable polished surfaces (Facette) on the sliding sleeve 16 and on the locking tooth 22.

In order to center the sliding sleeve 16 in its central position and to engage the respective synchronizing ring 20 with the friction surfaces assigned to it at the beginning of the shifting process, a plurality of support plates 30 are provided on the hub, which are inserted into corresponding recesses 32 of the hub 10. Three pallets are typically evenly distributed around the periphery of the hub 10.

Each support plate 30 has a detent element 34 in the form of a hardened ball which is acted upon by a spring 36 out of the pressure piece 30 and against an opposing surface 38 on the inside of the sliding sleeve 16, so that a detent surface 35 of the detent ball 34 (i.e. the surface of the detent ball) bears against it. As can be seen in particular in fig. 1 and 2, the opposing surface 38 is designed as a recess deepened outward in the radial direction, into which the latching element 34 engages when the sliding sleeve 16 is in its central position. In order to displace the sliding sleeve 16 in the axial direction, the detent elements 34 must be adjusted in the radial direction inward against the spring 36.

The detent element 34 is accommodated in a base body 40, which has a spring receptacle 42. The spring receptacle is provided with a base 44 on the side facing away from the latching element 34.

In order to prevent the locking element 34 from being pushed out of the main body 40 by the spring 36, the main body 40 is provided with a stop 46 on the side of the spring receptacle 42 facing away from the base 44. The stop 46 defines an opening that is smaller than the diameter of the latch element 34. Thus, only a portion of the spherical surface of the latching element 34 may project outwardly beyond the platform 30.

In fig. 4 and 5 an embodiment of a pallet according to the invention is shown. The same reference numerals are used for features known from fig. 1 to 3 and reference is made in this respect to the above description.

The difference between the support plate according to the invention and the support plate of fig. 1 to 3 is that in the support plate according to the invention, the detent elements 34 are not designed as balls, but rather have only hemispherical "outer sides" or detent surfaces 35 and an annular contact surface 50 for the spring 36 on the "rear side", i.e. on the side facing the bottom 44 of the base body 40.

A centering projection 52 is provided inside the contact surface 50. The spring no longer rests on the underside of the detent element 34 (and therefore no longer has a distance from the foremost point of its detent surface 35 that is close to the entire diameter of the detent ball 34), but rather rests on the flattened contact surface 50 and therefore has a distance of approximately half a diameter from the foremost point of the detent element 34 in the exemplary embodiment shown.

The centering bead 52 is here cylindrical and has a length, viewed in the axial direction of the spring 36, approximately equal to the diameter of the spherical base body of the detent element 34.

On the end facing away from the locking surface 35, the centering projection 52 is provided with a circumferential lead-in chamfer or chamfer.

Assuming that the usable spring length remains unchanged, the entire spring 36 can be pressed "closer" to the front side of the catch element 34 lying on the outside with approximately half the diameter of the catch element 34 using the solution according to the invention. In the case of a 5mm diameter detent ball, a reduction of the overall height of the spring in the order of almost 2mm is achieved in that the half diameter of the detent ball 34 is reduced by the immersion depth of the detent ball into the end face of the spring.

Rivets, turned parts or bases with hemispherical heads produced by other suitable machining processes can be used as base bodies for the latching elements 34. The base body of the locking element 34 is made here of a material having the strength and surface values required for the application. The latch elements may also be hardened, if desired.

Fig. 6 shows a latching element 34 for a carrier according to a second embodiment. The same reference numerals are used for features known from the first embodiment and reference is made in this respect to the above description.

The difference between the first and second embodiments is that in the second embodiment, the contact surface 50 for the spring 36 and the lead-in chamfer 60 coincide. The lead-in chamfer thus extends from the periphery of the latching surface 35 as far as the centering projection 52.

Similar to the first embodiment, the lead-in chamfer 60 is designed here as a conical chamfer.

Fig. 7 shows a latching element 34 for a carrier according to a third embodiment. The same reference numerals are used for features known from the first or second embodiment and reference is made in this respect to the above description.

In the third embodiment, a separate, annular abutment surface 50 for the spring 36 is again used.

Instead of a conical chamfer, the lead-in chamfer 60 is rounded here; the lead-in chamfer has an arbitrarily curved profile in cross section.

Due to the different radii, there is a circumferential transition from the large radius of the detent surface 35 to the smaller transition of the lead-in chamfer 60.

Fig. 8 shows a latching element 34 for a carrier according to a fourth embodiment. The same reference numerals are used for features known from the previous embodiments and reference is made in this respect to the above description.

The difference from the third embodiment is that a circumferential support surface 62 is present between the locking surface 35 and the lead-in chamfer 60. The support surface is designed here as a cylindrical surface centered with respect to the center axis of the latching element 34.

In comparison to the radius of the detent surface 35 of the previous embodiment, a larger radius is used here, so that the greater axial distance of the detent surface 35 from the contact surface 50 (i.e. further upwards with respect to the illustration in fig. 8) reaches the maximum diameter of the detent element 34. This results in an axial space for the support surface 62 at the same overall height.

The support surface 62 serves to better guide the lateral forces exerted by the sliding sleeve on the detent element into the carrier during shifting, since overall lower surface pressures (and thus an associated longer service life and an almost constant force level over the service life) are achieved.

Fig. 9 shows a latching element 34 for a pallet according to a fifth embodiment. The same reference numerals are used for features known from the previous embodiments and reference is made in this respect to the above description.

The difference between the fourth embodiment and the fifth embodiment is that in the fifth embodiment, a known, smaller radius is again used for the detent surface 35. It is also possible to use smaller radii.

In order to still have the necessary axial installation space for the circumferential support surface 62, a conical shoulder surface(s) is/are provided

) A shoulder surface 64, which adjoins the outer edge of the latching surface 35, which is designed here more flat in the axial direction, and leads to the support surface 62.

Instead of a tapered shoulder surface 64, any curved shoulder surface may be used.