DE1215450B - Pressure medium operated tooth clutch with a synchronization device - Google Patents

Description

Pressure fluid operated tooth coupling with a The invention relates a pressure medium-actuated synchronization device tooth coupling with a synchronization device, which consists of a pressure medium-actuated multi-plate clutch, that of the tooth clutch so assigned, is assigned that each coupling half has both teeth of the toothed coupling as also carries disks of the multi-disk clutch, with the one carrying the actuators The coupling half has a piston plate arranged immovably on a hub, which is sealingly surrounded by an axially displaceable actuating cylinder, the a sealed against the hub, forming the pressure plate for the multi-plate clutch Has end face, so that an engagement pressure space is formed.

In the known pressure medium-actuated tooth clutches with synchronization device, which consists of a pressure medium-actuated multi-plate clutch and serves to the speeds of the two clutch halves increase when the clutch is engaged synchronize before the X clutch teeth come into engagement the difficulty that the clutch teeth after the occurrence of synchronous running frequently therefore cannot indent because tooth stands before tooth. This will make the indentation the clutch not only made more difficult, but also a heavy wear of the teeth evoked.

There are already known clutches in which this difficulty is overcome by more or less complicated constructive measures.

In a known coupling there are pins and cam surfaces assigned to them provided on a compression ring to prevent slipping of the multi-plate clutch at the same time To effect engagement of the tooth clutch. This known device has relatively many and complicated individual parts that require very precise processing and which complicate the assembly and maintenance and adjustment of the clutch.

In another known clutch, the multi-plate clutch is first compressed by a piston acted upon by pressure medium, whereupon the teeth of the toothed clutch are brought into contact with one another via further secondary pistons mounted in the first piston. If these teeth are not in gap, the multi-disc clutch slips as soon as the torque of the drive shaft exceeds the holding force of the multi-disc clutch. As a result of this slippage in the multi-disc clutch , the teeth of the toothed clutch open up and slide into one another. This coupling also has a relatively large number of complicated individual parts.

In another known clutch are between the synchronizer and the coupling teeth of one coupling half are mutually adjustable in the direction of rotation Rings are provided which are connected to one another by approximately tangentially arranged, resilient elements are coupled. The synchronizing device also has two working together Ring gears between the two coupling halves. When the resilient elements are pressed together under the action of the torque, the teeth of the tooth coupling are on gap. This known coupling also has many complicated and moving ones Items on.

Finally, there is a hydraulically switchable tooth clutch with a plate pack used to synchronize the two tooth clutch halves is known, in which each coupling half has both teeth of the tooth coupling and the disks of the Multi-disc clutch carries. The coupling half carrying the actuators has a piston plate arranged immovably on a hub, which is supported by a axially displaceable actuating cylinder is sealingly surrounded, so that an engagement space. arises. The actuating cylinder has a sealed against the hub, which Pressure plate for the face forming the multi-plate clutch. In this known coupling is one of the ring gears of the gear clutch spring-loaded, and the pressure of the actuating cylinder is transmitted to the plate pack via a spring. If the teeth of the toothed clutch do not mesh with each other when engaging, the spring-loaded sprocket evade, while the spring between the Actuating cylinder and the disk pack allows the disk clutch to slip will. As soon as the teeth of the tooth coupling come to a gap, the tooth coupling becomes engaged by those springs on which the one ring gear is mounted. the The toothing of the clutch sprockets must be self-locking to prevent accidental To prevent disengagement of the tooth clutch.

- The invention has for its object to provide a gear coupling with synchronization device which is simple and compact in construction, but it ensures a particularly soft engagement process and a reliable lock. - The solution to this problem is achieved with a clutch of the type mentioned in that a second cylinder carrying one set of clutch teeth at one end is slidably arranged on the first actuating cylinder and is provided with a radial wall and thus with one with the first The piston wall connected to the actuating cylinder forms a second pressure space, the effective pressure area of which is larger than the effective area of the engagement pressure space of the first actuation cylinder acted upon by the pressure medium.

With such a toothed clutch, the clutch is engaged the engagement pressure chamber is initially acted upon, so that the first actuating cylinder the multi-plate clutch engages with its pressure plate until the speed of both Coupling halves is synchronized. At the same time, the second actuating cylinder moved in such a way that the toothed rings of the toothed coupling with their end faces against each other come to rest. When the second pressure chamber is subsequently acted upon, the first actuating cylinder lifted slightly from the disk pack, so that a Slip of the multi-disc clutch is possible. The teeth come through this slip the tooth coupling to stand on gap and slide into each other. You can see that a such a tooth coupling has an extremely simple and compact structure and at secure locking guarantees a soft engagement of the coupling teeth.

You can the second pressure chamber in the axial direction at a distance from Arrange engagement space when making an elongated, compact clutch want.

On the other hand, you can also radially next to the second pressure chamber Arrange the engagement pressure chamber to form a short, slightly wider clutch.

In one embodiment of the invention it is provided that separate pressure medium feeds, each provided with a control device, are provided for the engagement pressure space and for the second pressure space. In this case, the engagement process of the clutch can be controlled by appropriate actuation of the control device.

In another embodiment of the invention is a feed line arranged between the engagement pressure chamber and the second pressure chamber, through which the second pressure space is acted upon. This loading of the second pressure chamber takes place automatically at the right moment when this feed line from the engagement pressure chamber to the second pressure chamber has a small cross-section and in the first actuating cylinder is arranged so that it is in the disengaged position of the first actuating cylinder is closed by the circumference of an immovable piston plate.

The smooth engagement of the sprockets can be improved by that the teeth of the tooth capping are sawed off or rounded off at their front edges are.

The invention will now be explained with reference to exemplary embodiments, reference being made to the accompanying drawings.

F i g. 1 shows a longitudinal section through an embodiment of the coupling according to the invention in the disengaged position; F i g. FIG. 2 shows a partial section through the clutch according to FIG. 1, in which only the multi-plate clutch is in engagement; F i g. 3 is one of the F i g. 2 Corresponding section in which, after the second pressure chamber has been applied, the pressure on the clutch plates is released while the clutch teeth are not yet meshing with one another; F i g. 4 is one of the F i g. 3 corresponding section in which the coupling teeth mesh with one another; F i g. 5 shows a longitudinal section through another embodiment of the invention, in which the pressure spaces are arranged radially next to one another; F i g. 6 shows the embodiment according to FIG. 5 'with the multi-plate clutch engaged; F i g. 7 is one of the F ir g. 6 corresponding section in which, after the second pressure chamber has been acted upon, the clutch teeth touch but do not yet mesh with one another and the multi-disc clutch ring has just disengaged; F i g. 8 shows one of the FIGS. 7 corresponding section in which the coupling teeth mesh with one another.

The in F i g. The coupling shown in FIG. 1 has a driving coupling half E which is connected to a drive (not shown) by means of a drive shaft 10; A multi-disc clutch drum 11 is fastened to the drive shaft 10 by means of a toothing 12. On the inside of the drum 11 clutch plates 13 are attached in the usual way, which rotate with the drum.

At the free end of the drum 11 , a coupling ring 14 is arranged, the teeth of which protrude from the inside of the drum 11 radially inward.

The driven coupling half E1 has an output shaft 15 which is aligned with the drive shaft 10 and on the free end of which a pressure ring 16 is fastened. On the long hub 18 of the ring 16 clutch plates 17 are fixed which rotate together with the shaft 15 and the ring sixteenth

The lamellae 13, 17 can be axially pressed together with the support of the pressure ring 16 , so that frictional entrainment can be achieved. In the case of high-speed clutches of this type, the disks must be cooled in a known manner.

The driven coupling half EI also has a sleeve-shaped hub 20 with fluid channels, which is rigidly attached to the shaft 15. This hub 20 has a radially extending annular piston plate 21 which, together with an axially displaceable first actuating cylinder R, forms an engagement pressure chamber C. Relative rotation between the cylinder R and the piston plate 21 is prevented by pins 22 (only one of which is shown) which are fixed in the piston plate and on which the cylinder R slides.

The cylinder R has an end face 23 which forms the pressure plate for the multi-plate clutch and is connected to a radial intermediate wall 24 and a rearward radial piston wall 25 . The intermediate wall 24 and the sleeve 26 connecting the piston wall 25 to the cylinder R are sealed on the hub 20 and guided in a displaceable manner. The cylinder R has a smoothly machined outer cylinder surface 27.

The driven clutch half E 1 also has a second cylinder 30 which can be moved either to the left in the direction of an engaged position or to the right in a disengaged position by the application of pressure ( viewed in FIG. 1). The cylinder 30 has at one end a clutch ring gear 31, the teeth of which can come into engagement with the teeth 14 of the driving clutch half in order to engage the clutch.

The inner cylinder surface 32 of the cylinder 30 slides in a sealed manner on the cylinder surface 27 of the cylinder R. A cylindrical extension 33 with a larger diameter at the other end of the cylinder 30 slides in a sealed manner on the circumference 34 of the piston wall 25 connected to the cylinder R. In this way a pressure chamber C 1 is formed which enables a relative displacement between the first cylinder R and the second cylinder 30. Note that the pressure chamber C 1 a larger impingement: area than the crush space C.

Relative rotation between the first cylinder R and the second cylinder 30 is prevented by pins 35 which are fastened in the intermediate wall 24 and slide in recesses 36 in a radial central wall 37 of the cylinder 30.

Devices other than pins 22 and 35 can be used to avoid relative rotation between the various parts. In order to ensure a quick and correctly coordinated movement of the various parts, appropriate liquid outlets (not shown) can be provided, whereby liquid inclusion, for example in the recesses 36 , is avoided.

A sliding seal is provided between the various sliding parts in the form of known sealing rings 38 . Likewise, known snap rings 39 are used to prevent axial displacement if necessary.

Pressure medium, such as oil or air, is fed through the inlet 40 and the annular channel 41 into the engagement pressure chamber C and is supplied from a suitable pressure medium source (not shown) by opening a (not shown) control valve of a known type, this valve either operated manually or by other parts of the system in which the present clutch is used.

The space C 1 is acted upon by pressure medium via an axial channel 46, an opening 45, a wide annular channel 44, a passage 43 in the sleeve 26 and then through the recess 42. The pressure medium source (not shown) can be the same as that for the engagement pressure space C , and a suitable second control (not shown) is used to admit pressure medium into space C 1 at the appropriate moment and for the appropriate duration within the working cycle of the clutch .

The multi-disc clutch and the tooth clutch are operated as follows. The pressure medium is first admitted into the engagement pressure chamber C , so that the first cylinder R moves into the position in which it presses the lamellae 13, 17 together; in this way a frictional drive is established between the coupling halves E and E l ' , and these are brought to a synchronized speed. During this time, acceleration moments are present, and it is in the nature of the multi-plate clutch that it allows a certain amount of slippage, especially at the beginning of the clutch process. The axial movement of the first cylinder R to the left has also brought the second cylinder 30 close to the clutch teeth 14 on the drum 11 , and the teeth 14 and 31 are supposed to move as shown in FIG. Touch 2 right now. After the synchronization of the two coupling halves, they have stopped in any rotational position relative to one another, and in this state the teeth will normally not be ready to intervene in front of one another.

Pressure medium is now introduced into room C 1 either by hand control or as a result of a signal from another part of the system. It has already been mentioned that this second pressure space Cl has a larger pressure area than the engagement pressure space C , so that a common pressure medium source can be used. The introduction of the pressure medium into the space C 1 has the consequence that this tends to expand in the axial direction, whereby the ends of the coupling teeth 31 rest firmly against the ends of the possibly opposing teeth 14. As a result, the cylinder R is at that moment to the right ( Fig. 3), i.e. to the right. H. moved away from the plates 13, 17 , whereby the pressure on the plates is released and consequently the plate clutch can slip. This slipping causes the teeth 14 to move slightly in the direction of rotation with respect to the teeth 31 , so that the teeth come to mesh with one another. The second cylinder 30 is thereby immediately free and moves completely to the left ( FIG. 4) until the wall 37 rests against the shoulder 37-a of the cylinder R; the teeth 31 are pushed between the teeth 14.

If the coupling halves have immediately stopped relative to one another with gaps in the teeth, which can occasionally happen, then when the second pressure chamber C 1 is acted upon, the cylinder 30 is simply pushed into gear engagement immediately.

To disengage the clutch, chambers C and Cl are opened for emptying, and pressure medium is fed via the axial channel 47 and the opening 48 into the release pressure chamber 49, so that the cylinder R begins to move to the right. At the same time, the same pressure medium enters a further release pressure chamber 51 through the inlet 50 in order to withdraw the cylinder 30 (to the right in FIG. 1) with respect to the cylinder R.

In the coupling described above, two are acted upon one after the other Spaces provided that are arranged axially one behind the other. These Design results in an elongated but compact coupling.

In the above version, two controls are also provided, there is a time delay between the two.

In the case of the in FIG. 5 illustrated embodiment of the invention, two pressure chambers are arranged radially next to each other. In addition, a single control is used here, and the second pressure chamber is automatically acted upon by a movement of the first cylinder * during speed synchronization.

In Fig. 5 , the driving coupling half has a drum 100 which runs on a roller bearing 101 mounted on the shaft 102 of the driven coupling half. The driving clutch half also has - on fins 103, which are between the fins 104 of the driven clutch half. Coupling teeth 105 are formed at the free end of the drum 100. The lamellae are pressed by the axially displaceable first actuating cylinder R 1 against the pressure ring 106 attached to the free end of the shaft 102. A hub 107 is rigidly attached to the shaft 102 and has a piston plate 108 projecting radially outward.

The cylinder RI slides in a sealed manner on the hub 107 and has a radially outwardly projecting offset ring 109 which slides in a sealed manner on the circumference of the piston plate 108.

The cylinder R 1 with the piston plate 108 encloses an engagement pressure space, C 3. Pressure medium is introduced into this space via the opening and the axial bore 111 in the shaft 102.

Another opening 112 is formed in the cylinder R 1 , which is blocked when the clutch is in its in FIG. 5 shown disengagement is. When the cylinder R 1 moves a certain distance to the left, i. H. Moved in the direction of the position in which the multi-plate clutch is engaged, the opening 112 is released and the same pressure medium can enter a second pressure chamber C 4 via the intermediate space 115.

This second pressure space C4 is formed between the ring 109 of the cylinder R 1 and the second cylinder 117, the cylinder 117 sliding in a sealed manner on the ring 109 and the outside 118 of the first cylinder R 1 . The second cylinder 117 also has a rear radial wall 119 which slides on the hub 107 in a sealed manner.

Coupling teeth 120, which can be brought into mesh with the teeth 105 of the drum 100 , are formed at the end of the second cylinder 117.

A Ausrückdruckraum 130 is from the second cylinder 117, the outer piston wall 116 of the ZY Linders R 1 and the piston plate 108 of the hub 107 is enclosed. In this space 130 pressure medium Ube, r, an opening 133 and a channel 1134 can enter so as to cause the retraction of the second cylinder 117 (to the right) and then the retraction of the first cylinder R 1.

Pins 136 and 137 conventionally prevent relative rotation between their associated parts. Known sliding seals 138 are also used at the locations indicated. * A check valve 104 with a spring-mounted ball allows the pressure medium to flow quickly from space C 4 back into space C 3. Note that space C 4 has a larger area under pressure for the pressure medium than space C 3.

If the coupling did not differ from the one shown in FIG. 5 is to be brought into the engagement position, pressure medium is admitted into the space C3 , whereby the multi-plate clutch is pushed into engagement and the teeth 120 are pushed into the immediate vicinity of the teeth 105 (FIG. 6). This movement of the cylinder R 1 exposes the opening 112 and pressure medium can then slowly enter the space C 4.

The loading of space C4 causes teeth 120 to rest firmly against teeth 105 (Fig . 7), and the axial force in space C 4 then becomes greater than the axial force in space C 3. This causes the first cylinder R1 to be withdrawn very easily and briefly so that the LameHenkupplung slips for a short time; the coupling teeth 105, 120 can align with one another. The cylinder 117 then slides vigorously into the engagement position (FIG . 8) in which the radial wall 119 rests against the piston wall 116 .

The coupling teeth of the coupling halves can be bevelled or rounded at their opposite edges to facilitate the meshing of the teeth; however, this does not prevent the teeth from colliding and not combing due to incorrect alignment . These teeth can also be designed in such a way that they generate a suction pressure when combing , which holds the teeth in engagement with one another and prevents them from accidentally sliding apart if the pressure medium system fails.

. In the exemplary embodiments, the two pressure chambers for engaging the clutch are axially one behind the other ( FIG. 1) or radially next to one another ( FIG. 5) with two pressure medium feeds ( FIG. 1) or one pressure medium feed (F i g. 5) shown; it goes without saying, however, that a single pressure medium supply and a single control device can also be used in the arrangement of the pressure spaces. according to FIG. 1 or two control systems in the radial juxtaposition of the pressure chambers according to FIG . 5 could be used.

Claims (2)

Claims: 1. Pressure medium-actuated tooth coupling with a synchronization device, which consists of a pressure-medium actuated Lameffenkupplung, which is assigned to the tooth coupling in such a way that each coupling half carries both teeth of the tooth coupling and plates of the multi-plate coupling, the coupling half carrying the actuating elements having a piston plate which is immovable on the hub which is sealingly surrounded by an axially displaceable operating cylinder, which has a relative to the hub sealed, the pressure plate forming the multi-disc clutch face side so that a Eindrückdruckraum is formed, characterized in 'that on the first actuating cylinder (R, 27 and R 1 ) a second cylinder (30 or 117 ) carrying one set of coupling teeth (31 or 120) is slidably arranged at one end and is provided with a radial wall (37) and is thus connected to one of the first actuating cylinders Piston wall (25 or 116) forms a second pressure chamber (C 1 or C 4), the effective pressure area of which is larger than the effective area of the engagement pressure chamber (C or C3) of the first actuating cylinder acted upon by the pressure medium. 2. Tooth coupling according to claim 1, characterized in that the second pressure chamber (C1) is arranged in the axial direction at a distance from the engagement pressure chamber (C). 3. Tooth coupling according to claims 1 or 2, characterized in that separate, each provided with a control device pressure medium feeds (40, 41; 42 to 46) for the engagement pressure chamber (C) and for the second pressure chamber (C1) are provided. 4. Tooth coupling according to claim 1, characterized in that the second pressure chamber (C 4) is arranged radially next to the engagement pressure chamber (C 3) . 5. Tooth coupling according to claims 1 or 4, characterized in that a feed line (112, 114) is arranged between the engagement pressure chamber (C3) and the second pressure chamber (C4). 6. Tooth coupling according to claim 5, characterized in that the feed line (112, 115) has a small cross section and is arranged in the first actuating cylinder (R 1) so that it is in the disengaged position of the first actuating cylinder from the circumference of an immovable piston plate (108) is closed. 7. Tooth coupling according to one of the preceding claims, characterized in that the teeth (14, 31 or 105, 120) of the tooth coupling are beveled or rounded at their front edges. Considered publications: German utility model No. 1820 096; USA. Patent Nos. 2,633,955, 3,048,247, 3,071,224th