DE102018204490A9 - Double-split gear-return switch with a Trennsynchronisiereinrichtung - Google Patents

Abstract

A transmission return switch for reversing a direction of a driven wheel carried by an output shaft includes a return shaft, a reverse clutch mounted around the return shaft having engaged and disengaged states, and a reverse slip synchronizer supported about the return shaft and having engaged and disengaged states , When the reverse clutch and the retrace separating synchronizer are in the engaged states, the return shaft rotates the driven gear in a reverse rotational direction against the rotational direction of the output shaft. When the reverse disconnect synchronizer is in the disengaged state, the reverse clutch is disconnected from the output gear.

Description

CROSS REFERENCE TO RELATED APPLICATION (S)

This is a continuation submission application of the pending application with patent no. 15 / 049,629, filed on February 22, 2016.

STATEMENT OF RESEARCH FUNDED BY THE ASSOCIATION OR

DEVELOPMENT

Does not find any applications.

AREA OF REVELATION

The present disclosure generally relates to transmissions having a return switch for changing the direction of a vehicle.

GENERAL STATEMENT OF THE DISCLOSURE

Gears are used, for example, in vehicles or work machines, such as in agricultural, construction, off-highway and industrial machinery. Gears used in work machines typically provide a large number of gear ratios for driving the vehicle. A transmission may include a return switch for changing the directions of the vehicle. The return switch may be located near the transmission output. In some previous embodiments, a balance shaft return switch rotates at high speeds when the vehicle is operating at high forward speeds. This can lead to strong air movement in the reverse clutch. This can also cause gyroscopic flutter, in which the friction disc or the separation plate becomes dynamically unstable, creating a resistance in the clutch. This resistance can cause the disengaged clutch to have a thermal fault. In other previous embodiments, a synchronized return switch will go to idle when switching between forward and reverse, causing an acceleration pause.

SHORT DESCRIPTION OF THE REVELATION

This summary is provided to introduce a selection of concepts that are further described below in the detailed description and the accompanying drawings. This summary is not intended to identify key or main features of the appended claims, nor is it intended to be used as an aid in determining the scope of the appended claims.

According to one aspect of the present disclosure, a transmission return switch for reversing a direction of a driven wheel carried by an output shaft may include a return shaft, a reverse clutch mounted around the return shaft having engaged and disengaged states, and a reverse disconnecting synchronizer connected about the return shaft stored and has engaged and disengaged states include. When the reverse clutch and the retrace separating synchronizer are in the engaged states, the return shaft rotates the driven gear in a reverse rotational direction against the rotational direction of the output shaft. When the reverse disconnect synchronizer is in the disengaged state, the reverse clutch is disconnected from the output gear.

According to another aspect of the present disclosure, for reversing a direction of a driven gear carried by an output shaft, a transmission return switch may include a return shaft extending along an axis of rotation, comprising return wheels disposed about the Return shaft are mounted, comprise a reverse clutch, which is mounted around the return shaft with engaged and disengaged states and a return wheel with the return shaft in the engaged state and a Rücklauf Trennsynchronisiereinrichtung comprise, which has engaged and disengaged states that another return wheel with the Return shaft in the engaged state connects. The return separation synchronizer includes a hub that is supported about the return shaft and defines a piston chamber. An actuating piston in the piston chamber is driven by fluid pressure in at least one direction along the axis of rotation of the return shaft. A shift sleeve is mounted on the actuating piston and engaged with the return wheel in an engaged state. When the reverse clutch and the retrace separating synchronizer are in the engaged states, the return shaft rotates the driven gear in a reverse rotational direction against the rotational direction of the output shaft. When the reverse disconnect synchronizer is in the disengaged state, the reverse clutch is disconnected from the output gear.

According to another aspect of the present disclosure, for reversing a direction of a driven wheel carried by an output shaft, a transmission return switch may include a return shaft extending along an axis of rotation, comprising return wheels supported about the return shaft, a reverse clutch surrounding the return shaft Return shaft is mounted with engaged and disengaged states and connects a return wheel with the return shaft in the engaged state and comprise a Rücklauf-Trennsynchronisiereinrichtung having engaged and disengaged states and connects another return wheel with the return shaft in the engaged state. The retrace separation synchronizer includes an actuating piston having a first annular surface with a first locking feature and a sliding sleeve engaged with the return wheel in an engaged state and having a second annular surface with a second locking feature configured to mate with the first locking feature the actuating piston is engaged. The shift collar is connected to the actuating piston by overlapping radial surfaces of the first and second locking features when the first and second annular surfaces are concentrically disposed. When the reverse clutch and the retrace separating synchronizer are in the engaged states, the return shaft rotates the driven gear in a reverse rotational direction against the rotational direction of the output shaft. When the reverse disconnect synchronizer is in the disengaged state, the reverse clutch is disconnected from the output gear.

These and other features will become apparent from the following detailed description and the accompanying drawings, in which various features are shown and described by way of illustration. The present disclosure may have other and different configurations, and its various details may be changed in various other respects without departing from the scope of the present disclosure. Accordingly, the detailed description and the attached drawings are to be considered as illustrative rather than limiting or restrictive.

list of figures

• 1 eine perspektivische Ausschnittsansicht eines Getriebes gemäß einer Ausführungsform ist;
• 2 eine perspektivische Rückansicht eines Getriebes gemäß einer Ausführungsform ist;
• 3 eine seitliche Schnittansicht eines Rücklaufschalters gemäß einer Ausführungsform ist;
• 4 eine seitliche Schnittansicht eines Rücklaufschalters ist, die den Leistungspfad für den Vorwärtsmodus gemäß einer Ausführungsform darstellt;
• 5 eine seitliche Schnittansicht eines Rücklaufschalters ist, die den Leistungspfad für den Rückwärtsmodus gemäß einer Ausführungsform darstellt;
• 6 ein schematisches Diagramm einer Steuerstrategie für ein Getriebe gemäß einer Ausführungsform ist;
• 7 ein Ablaufdiagramm ist, das ein Verfahren zum Umschalten zwischen Vorwärts- und Rückwärtsrichtungen in einem Getriebe-Rücklaufschalter gemäß einer Ausführungsform darstellt;
• 8 ein Ablaufdiagramm ist, das ein Verfahren zum Umschalten zwischen Rückwärts- und Vorwärtsrichtungen in einem Getriebe-Rücklaufschalter gemäß einer Ausführungsform darstellt;
• 9 eine seitliche Schnittansicht eines Rücklaufschalters ist, die den Leistungspfad für den Vorwärtsmodus gemäß einem zweiten Ausführungsbeispiel darstellt;
• 10 eine seitliche Schnittansicht eines Rücklaufschalters ist, die den Leistungspfad für den Rückwärtsmodus gemäß dem zweiten Ausführungsbeispiel darstellt;
• 10A eine vergrößerte Ansicht einer exemplarischen Trennsynchronisieranordnung für einen Rücklaufschalter gemäß der zweiten Ausführungsform ist;
• 10B eine detaillierte Ansicht des Bereichs 10B-10B einer Schnittstelle zwischen einem Betätigungskolben und einer Schaltmuffe der in 10A gezeigten Trennsynchronisiereinrichtung ist;
• 11 ein schematisches Diagramm eines Steuersystems für ein Getriebe gemäß dem zweiten Ausführungsbeispiel ist;
• 11A ein schematisches Diagramm einer Steuerstrategie für ein Getriebe gemäß der zweiten Ausführungsform ist;
• 12 ein Ablaufdiagramm ist, das eine exemplarische Startsequenz für einen Getriebe-Rücklaufschalter gemäß der zweiten Ausführungsform darstellt;
• 13 ein Ablaufdiagramm ist, das ein exemplarisches Verfahren zum Umschalten zwischen Vorwärts- und Rückwärtsrichtungen in einem Getriebe-Rücklaufschalter gemäß einer zweiten Ausführungsform darstellt;
• 13A ein Ablaufdiagramm ist, das ein exemplarisches Logik-Unterprogramm zum Steuern des Eingriffs einer Trennsynchronisiereinrichtung in dem Verfahren von 13 darstellt;
• 14 ein Ablaufdiagramm ist, das ein exemplarisches Verfahren zum Umschalten zwischen Rückwärts- und Vorwärtsrichtungen in einem Getriebe-Rücklaufschalter gemäß einer zweiten Ausführungsform darstellt;
• 14A ein Ablaufdiagramm ist, das ein exemplarisches Steuerlogik-Unterprogramm zum Steuern des Eingriffs oder Ausgriffs der Trennsynchronisiereinrichtung in dem Verfahren von 14 darstellt; und
• 14B ein Ablaufdiagramm ist, das ein exemplarisches Steuerlogik-Unterprogramm zum Erfassen eines Fehlers beim Ausgriff der Trennsynchronisiereinrichtung in dem Verfahren von 14 darstellt.

The detailed description of the drawings refers to the attached figures, in which:

• 1 a partial perspective view of a transmission according to an embodiment;
• 2 a rear perspective view of a transmission according to an embodiment;
• 3 a side sectional view of a return switch according to an embodiment;
• 4 FIG. 4 is a side sectional view of a flyback switch illustrating the forward mode power path according to an embodiment; FIG.
• 5 Figure 4 is a side sectional view of a flyback switch illustrating the power path for the reverse mode according to one embodiment;
• 6 FIG. 12 is a schematic diagram of a control strategy for a transmission according to an embodiment; FIG.
• 7 FIG. 10 is a flowchart illustrating a method of switching between forward and reverse directions in a transmission reverse switch according to an embodiment; FIG.
• 8th FIG. 10 is a flowchart illustrating a method of switching between reverse and forward directions in a transmission reverse switch according to an embodiment; FIG.
• 9 FIG. 4 is a side sectional view of a flyback switch illustrating the power path for the forward mode according to a second embodiment; FIG.
• 10 is a side sectional view of a return switch, which represents the power path for the reverse mode according to the second embodiment;
• 10A Fig. 10 is an enlarged view of an exemplary disconnect synchronizer assembly for a flyback switch according to the second embodiment;
• 10B a detailed view of the area 10B - 10B an interface between an actuating piston and a sliding sleeve of in 10A shown Trennsynchronisiereinrichtung is;
• 11 Fig. 10 is a schematic diagram of a control system for a transmission according to the second embodiment;
• 11A FIG. 12 is a schematic diagram of a control strategy for a transmission according to the second embodiment; FIG.
• 12 FIG. 10 is a flowchart illustrating an exemplary start-up sequence for a transmission reverse switch according to the second embodiment; FIG.
• 13 FIG. 10 is a flowchart illustrating an exemplary method of switching between forward and reverse directions in a transmission reverse switch according to a second embodiment; FIG.
• 13A 5 is a flowchart illustrating an exemplary logic subroutine for controlling the engagement of a separation synchronizer in the method of FIG 13 represents;
• 14 FIG. 10 is a flowchart illustrating an exemplary method of switching between reverse and forward directions in a transmission reverse switch according to a second embodiment; FIG.
• 14A 5 is a flow chart illustrating an exemplary control logic subroutine for controlling the engagement or extraction of the separation synchronizer in the method of FIG 14 represents; and
• 14B FIG. 10 is a flow chart illustrating an exemplary control logic subroutine for detecting an error in the extraction of the separation synchronizer in the method of FIG 14 represents.

Like reference numerals are used to designate like elements throughout the several figures.

DETAILED DESCRIPTION

The embodiments disclosed in the above drawings and the following detailed description are not intended to be exhaustive or to limit the disclosure to those embodiments. Rather, there are several variations and modifications that can be made without departing from the scope of the present disclosure.

1 shows, for example, a transmission 100 for a vehicle or work machine, such as a tractor. The present disclosure also applies to other powered or motorized vehicles, machines or equipment. The gear 100 includes a housing 102 forming an interior space providing an enclosure for one or more transmission components, including but not limited to shafts, gears, clutches and synchronizers. The gear 100 may be a gear-return switch device 110 include, which switches the transmission output between the forward and reverse gears. The return switch 110 can with the gear 100 be integrated or separate from this.

The 2 and 3 show a gearbox 100 with a return switch device 110 which may comprise one or more of the following components. The gear 100 can be an output shaft 112 , an idle shaft 114 and a countershaft 116 include, which is rotatable with the transmission housing 102 are connected. The gear 100 can be a first return wheel 120 and a driven wheel 122 include that on the output shaft 112 is arranged or stored. The driven wheel 122 is operatively connected to the drivetrain of a vehicle that provides power to a ground engaging device, such as wheels or rails. The transmission can be an idle wheel 124 include that on the idle shaft 114 is arranged or stored. The transmission can be a second return wheel 126 and a third return wheel 128 include that on the countershaft 116 are arranged or stored. The gear 100 can be a forward clutch 130 include the output gear 122 with the output shaft 112 operatively connect or couple in an engaged position or an engaged state. The forward clutch 130 can with the output shaft 112 be connected or stored around this.

The gear 100 can be a reverse clutch 132 include the second return wheel 126 with the countershaft 116 operatively connect or couple in an engaged position or an engaged state. The reverse clutch 132 can with the countershaft 116 be connected or stored around this. In another embodiment, the reverse clutch connects or couples 132 the first return wheel 120 with the output shaft 112 functioning. The reverse clutch 132 can with the output shaft 112 be connected or stored around this. In this embodiment, the output shaft rotates 112 independent of the first return wheel 120 , the idle wheel 124 and the idle shaft 114 when the reverse clutch 132 is disengaged. The gear 100 can a disconnect clutch 134 include the third return wheel 128 with the countershaft 116 operatively connect or couple in an engaged position or an engaged state. The separating clutch 134 can with the countershaft 116 be connected or stored around this. The first return wheel 120 is with the idle wheel 124 engaged or meshed with this, which with the second return wheel 126 indented or meshed with this. The third return wheel 128 is with the output gear 122 indented or interlocked with this. The gear 100 can be a countershaft brake 136 include the rotation of the countershaft 116 reduced or stopped in an engaged position or an engaged state. In some embodiments, the countershaft brake may 136 the countershaft 116 prevent rotation or stop rotation. This can hinder or stop the reverse clutch 132 turns when the countershaft brake 136 is indented.

4 shows a power path or flow for a forward mode F through the return switch device 110 , In the forward mode F is the forward clutch 130 indented, which causes the output gear 122 with the output shaft 112 rotates. The countershaft brake 136 is engaged, indicating the rotation of the countershaft 116 hinders or stops, and the reverse clutch 132 and the disconnect clutch 134 are disengaged. If the countershaft brake 136 This can also be the rotation of the reverse clutch 132 hinder or stop. The idle shaft 114 turns opposite to the output shaft 112 based on the ratio of the first return wheel 120 to the idle wheel 124 , The second return wheel 126 revolves around the countershaft 116 in an idle shaft 114 opposite direction based on the ratio of the idle wheel 124 to the second return wheel 126 , At slow forward speeds, the countershaft brake can 136 be disengaged and the disconnect clutch 134 be indented, which causes the countershaft 116 in the output shaft 112 opposite direction based on the ratio of the driven wheel 122 to the third return wheel 128 rotates. In some embodiments, the slow forward speeds are at or below about 5 km / h, 4 km / h, 3 km / h, 2 km / h or 1 km / h.

5 shows a power path or flow for a reverse mode R through the return switch device 110 , In the reverse mode R are the reverse clutch 132 and the disconnect clutch 134 indented, which causes the output gear 122 in a to the output shaft 112 turns opposite direction. The forward clutch 130 and the countershaft brake 136 are disengaged. The driven wheel 122 turns opposite to the countershaft 116 based on the ratio of the third return wheel 128 to the driven wheel 122 , The countershaft 116 turns opposite to the idle shaft 114 based on the ratio of the idle wheel 124 to the second return wheel 126 , The idle shaft 114 turns against the output shaft 112 based on the ratio of the first return wheel 120 to the idle wheel 124 , As a result, the countershaft is spinning 116 in the same direction as the output shaft 112 ,

6 FIG. 12 shows a control strategy for a transmission that may be implemented in one or more of the embodiments described herein and illustrated in the various figures. When the transmission is in reverse R mode, the reverse clutch is on 132 and the disconnect clutch 134 engaged and the forward clutch 130 and the countershaft brake 136 disengaged. When switching between the reverse mode R and the forward mode F For example, events may occur in the following order: the reverse clutch 132 is disengaged, the forward clutch 130 is engaged, the disconnect clutch 134 is disengaged and the countershaft brake 136 is engaged. The reverse clutch 132 and the forward clutch 130 can be engaged and disengaged at slow reverse speeds, slow forward speeds, or when the vehicle is not moving.

When the transmission is in forward mode F are the forward clutch 130 and the countershaft brake 136 engaged and the reverse clutch 132 and the disconnect clutch 134 disengaged. When switching between the forward mode F and the reverse mode R For example, events may occur in the following order: the countershaft brake 136 is disengaged, the disconnect clutch 134 is engaged, the forward clutch 130 is disengaged and the reverse clutch is engaged. The separating clutch 134 and the countershaft brake 136 can be engaged and disengaged at slow forward speeds, or when the vehicle is not moving.

7 FIG. 10 is a flowchart for a method of switching between a forward mode and a reverse mode in a transmission retrace switch according to an embodiment that may be implemented in one or more of the embodiments described herein and the figures illustrated. The procedure starts with step 200 ,

At step 202 the transmission is in the forward mode F with the forward clutch 130 and the countershaft brake 136 in the engaged states.

At step 204 the transmission receives a command to switch from the forward mode F to the reverse mode R.

At step 206 becomes the countershaft brake 136 disengaged, causing the countershaft 116 can turn.

At step 208 becomes the disconnect clutch 134 indented, which is the third return wheel 128 detachable with the countershaft 116 connects or couples, which causes the countershaft 116 in the output shaft 112 opposite direction based on the engagement of the third return wheel 128 with the driven wheel 122 rotates.

At step 210 becomes the forward clutch 130 disengaged, causing the output gear 122 from the output shaft 112 is disconnected, so that the output gear 122 independent of the output shaft 112 can turn.

At step 212 is the reverse clutch 132 indented, which is the second return wheel 126 detachable with the countershaft 116 connects or couples, which causes the countershaft 116 in the output shaft 112 same direction based on the engagement of the first return wheel 120 that is on the output shaft 112 is stored, with an idle wheel 124 that on an idle shaft 114 is stored, and the engagement of the idle wheel 124 with the second return wheel 126 rotates.

In an alternative step 212 is the reverse clutch 132 indented, which is the first return wheel 120 detachable with the output shaft 112 connects or couples, which causes the countershaft 116 in the output shaft 112 same direction based on the engagement of the first return wheel 120 with the idle wheel 124 that on the idle shaft 114 is stored, and the engagement of the idle wheel 124 with the second return wheel 126 that is on the output shaft 116 is stored, turns.

At step 214 For example, the method of switching between a forward mode and a reverse mode in a transmission reverse switch according to one embodiment is completed. In other embodiments, one or more of these steps or operations may be omitted, repeated or changed, and still achieve the desired results.

8th FIG. 10 is a flowchart for a method of switching between a reverse mode and a forward mode in a transmission retrace switch according to an embodiment that may be implemented in one or more of the embodiments described herein and the figures illustrated. The procedure starts with step 200 ,

At step 202 the gearbox is in reverse mode R with the reverse clutch 132 and the disconnect clutch 134 is in the engaged states.

At step 204 the transmission receives a command to switch from the reverse mode R to the forward mode F ,

At step 206 is the reverse clutch 132 disengaged, creating the second return wheel 126 from the countershaft 116 is disconnected or the first return wheel 120 from the output shaft 112 separates, causing the countershaft 116 independent of the output shaft 112 can turn.

At step 208 is the forward clutch 130 indented, which is the output gear 122 detachable with the output shaft 112 connects or couples, which causes the output gear 122 with the output shaft 112 rotates.

At step 210 becomes the disconnect clutch 134 disengaged, creating the third return wheel 128 from the countershaft 116 is disconnected, so that the countershaft 116 independent of the output gear 122 can turn.

At step 212 is the countershaft brake 136 indented, causing the rotation of the countershaft 116 slowed down or stopped. In some embodiments, the countershaft brake may 136 the countershaft 116 then stop turning or stop rotation.

At step 214 For example, the method of switching between a reverse mode and a forward mode in a transmission reverse switch according to one embodiment is completed. In other embodiments, one or more of these steps or operations may be omitted, repeated or changed, and still achieve the desired results.

At step 214 For example, the method of switching between a reverse mode and a forward mode in a transmission reverse switch according to one embodiment is completed. In other embodiments, one or more of these steps or operations may be omitted, repeated or changed, and still achieve the desired results.

Now, another embodiment of the transmission-return switch disclosed herein will be described. It is understood that this embodiment of the transmission-return switch can be installed in a transmission for a vehicle or a work machine (or other equipment). The gear 100 For example, this embodiment of the transmission-return switch can incorporate and the same configuration as with respect to those illustrated and described above 1 and 2 unless otherwise stated, including a housing 102 forming an interior space providing an enclosure for one or more transmission components, including but not limited to shafts, gears, clutches and synchronizers. As described in the previous embodiment, this embodiment of the transmission-return switch can be used to switch the transmission output between the forward and reverse gear and can with the transmission 100 integrated or separate from it.

The 9 and 10 show a return switch device 300 which may include one or more of the following components, including an output shaft 302 , an idle shaft 304 and a return shaft in the form of a countershaft 306 moving along a rotation axis " A "Extends, each rotatable with the gearbox 102 are connected. The gear 100 or the return switch device 300 can be a first rear wheel 310 and a driven wheel 312 include that on the output shaft 302 is arranged or stored. The driven wheel 312 may be operatively connected to the drivetrain of a vehicle providing power to a ground engaging device such as wheels or rails. The gear 100 or the return switch device 300 can be an idle wheel 316 include that on the idle shaft 304 is arranged or stored and a second return wheel 318 and a third return wheel 320 that on the countershaft 306 is arranged or stored. The gear 100 or the return switch device 300 can be a forward clutch 330 include the output gear 312 with the output shaft 302 operatively connect or couple in an engaged position or an engaged state. The forward clutch 330 can with the output shaft 302 be connected or stored around this. The gear 100 or the return switch device 300 can be a reverse clutch 332 include the second return wheel 318 with the countershaft 306 operatively connect or couple in an engaged position or an engaged state. As described in the previous embodiment, in this embodiment, the reverse clutch 332 with the countershaft 306 be connected or stored around this, so that the countershaft 306 regardless of the first reverse 310 , the idle wheel 316 and the idle shaft 304 turns when the reverse clutch 332 is disengaged. In another embodiment, the reverse clutch connects or couples 332 the first return wheel 310 with the output shaft 302 functional, in which case the reverse clutch 332 with the output shaft 302 may be connected or mounted around these, so that the output shaft 302 regardless of the first reverse 310 , the idle wheel 316 and the idle shaft 304 turns when the reverse clutch 332 is disengaged.

The gear 100 or the return switch device 300 This embodiment comprises a separation synchronizer 340 that the third return wheel 320 with the countershaft 306 operatively connect or couple in an engaged position or an engaged state. The separation synchronizer 340 can with the countershaft 306 be connected or stored around this. The first return wheel 310 is with the idle wheel 316 engaged or meshed with this, which with the second return wheel 318 indented or meshed with this. The third return wheel 320 is with the output gear 312 indented or interlocked with this. In this embodiment, the transmission 100 or the return switch device 300 omit a countershaft brake, which was used in the previous embodiment to the rotation of the countershaft 306 to reduce or stop in an engaged position or an engaged state, thereby rotating the reverse clutch 332 to hinder or stop. Alternatively, a countershaft brake in the transmission 100 or the return switch device 300 built in this embodiment, such as the countershaft brake 136 , and used for the purpose mentioned.

9 shows a power path or flow for a forward mode F through the return switch device 300 , In the forward mode F is the forward clutch 330 indented, which causes the output gear 312 with the output shaft 302 turns and the reverse clutch 332 (and at times the Trennsynchronisiereinrichtung 340 ) are disengaged. (The countershaft brake, if present, can be engaged, thereby preventing the countershaft from being caught 306 and the reverse clutch 332 turn.) The idle shaft 304 turns opposite to the output shaft 302 based on the ratio of the first return wheel 310 to the idle wheel 316 , The second return wheel 318 revolves around the countershaft 306 in an idle shaft 304 opposite direction based on the ratio of the idle wheel 316 to the second return wheel 318 , At slow forward speeds, the separation synchronizer 340 be indented, which causes the countershaft 306 in the opposite direction as the output shaft 302 based on the ratio of the driven wheel 312 to the third return wheel 320 rotates. (The countershaft brake, if present, would be disengaged.) As in the previous embodiment, the slow forward speeds may be at or below about 5 km / h, 4 km / h, 3 km / h, 2 km / h or 1 km / h lie.

10 shows a power path or flow for a reverse mode R through the return switch device 300 , In the reverse mode R are the reverse clutch 332 and the separation synchronizer 340 indented, which causes the output gear 312 in a to the output shaft 302 turns opposite direction. The forward clutch 330 (and, if present, the countershaft brake) is disengaged. The driven wheel 312 turns opposite to the countershaft 306 based on the ratio of the third return wheel 320 to the driven wheel 312 , The countershaft 306 turns opposite to the idle shaft 304 based on the ratio of the idle wheel 316 to the second return wheel 318 , The idle shaft 304 turns against the output shaft 302 based on the ratio of the first return wheel 310 to the idle wheel 316 , As a result, the countershaft is spinning 306 in the same direction as the output shaft 302 ,

The separation synchronizer may be configured in various ways. For example, certain known synchronizers are engaged and disengaged by the movement of a shift rail and fork assembly that can be manually or semi-automatically actuated. In general, in such cases, one or more fork members ride along one or more shift rails to engage a synchronizer with a gear of the transmission (eg, by interlocking the synchronizer teeth with the gear teeth). The synchronizer is coupled to the shaft for co-rotation, and thus the engagement of the synchronizer with the gear also couples the gear to the shaft for co-rotation, thereby rotating the gear into the rotational power (or torque) path from the power source (e.g. B. a motor) is received. A locking member may be disposed between the synchronizing member and the gear to prevent displacement until its splines are clocked to be offset with the splines of the gear. The engagement and disengagement of the gear can thus be largely, if not completely, mechanical in the sense that the shift rail reciprocates the synchronizer with respect to the gear. Certain other known synchronizers have been developed which use hydraulic force to couple gear sets to the output shaft. Some of these use a shift rail and fork assembly similar to that described above, although the shift fork movement is hydraulically effected. Other systems completely eliminate the shift rail and fork assembly. Instead, these systems direct hydraulic fluid into chambers that drive pistons to engage shift sleeves with the gears. A shift collar is disengaged from a gear by venting a pressure chamber such that one or more return springs acting on the piston can move the shift collar back to a neutral position. The reverse gear may also be true, in that the spring exerts the engagement force on the shift sleeve, which is then hydraulically disengaged. Still other synchronizers can be used which are fully electro-hydraulically operated so that the displacement of the shift sleeves into both the engaged and the take-off positions is by hydraulic force. Furthermore, the Trennsynchronisiereinrichtung be on or double-sided, with either one or two gears can be engaged with the shaft.

As an example, this embodiment of the return switch device 300 described, wherein the separation synchronizer 340 is configured as a one-sided (or "half") fork-free synchronizer which is hydraulically engaged and disengaged by spring force. Although not shown, it is understood that the work vehicle, the transmission 100 or the return switch device 300 an electro-hydraulic system having one or more hydraulic pumps and electrohydraulic valves controlled by one or more controls for controlling operating modes of the transmission 100 or the return switch device 300 operated, includes or is in functional connection with it. In general, the exemplary separation synchronizer is 340 operable to selectively the third return wheel 320 with the countershaft 306 and thereby the reverse clutch 332 with the driven wheel 312 to couple depending on the control logic associated with the mode of operation of the transmission, as mentioned above and described in detail below.

10A shows the exemplary semi-fork-free hydraulic Trennsynchronisiereinrichtung 340 , The separation synchronizer 340 can with the countershaft 306 through a drum 342 or the like connected to or mounted on the, which is continuous on the countershaft 306 is supported for a co-rotation, such as on the counter-spline or other Gegenverzahnungs- or polygonal sections of the countershaft 306 and the drum 342 , The drum 342 defines a stepped annular piston space 344 in which hydraulic fluid can be steered in a controlled manner to an actuating piston 346 to move along the axis of rotation A. The actuating piston 346 has a stepped outer periphery to the piston chamber 344 adapted to be and is sealed at both stepped diameters (via O-rings or the like). The sliding sleeve 348 has an axially toothed inner diameter, which is provided with an axially toothed periphery (circumferential or circumferential segments) of a hub 350 is connected, which has an axially toothed inner diameter, with splines on the countershaft 306 intervenes. The hub 350 has open areas in which Halterfederrastanordnungen 352 (each with a spring 354 , a ball 356 and a ball cuff 358 ), with the hub 350 are coupled (eg., By retaining pins of the ball cuff 358 or attached to this holding pins). The balls 356 the spring detent arrangements 352 run in an annular groove 368 in the toothed inner diameter of the sliding sleeve 348 and apply a spring force to a locking ring 370 off when the shift sleeve 348 initially axially relative to the hub 350 is switched. An annular body of the locking ring 370 is inside an annular, open-sided pocket 372 in the hub 350 axially between the third return wheel 320 and the hub 350 arranged. The locking ring 370 turns with the hub 350 but may slightly "slide" or move relative to the hub 350 rotate, for example by a pin and slot connection (not shown) of the locking ring 370 with the hub 350 , The locking ring 370 has a tapered inner circumference with a conical ring or cone 374 connected to the third return wheel 320 attached or can be integrally formed with this. In certain embodiments, the taper of the locking ring 370 or the gear cone 374 a thin friction ring 360 include (eg, by gluing) to assist in the production of a robust friction joint, and cooling grooves (not shown) may be incorporated into the friction ring 360 be shaped to assist in heat dissipation. The locking ring 370 also has an axially toothed outer ring (or ring segments), which with the toothed inner diameter of the sliding sleeve 348 engages. The drum 342 , the actuating piston 346 , the shift sleeve 348 , the hub 350 and the locking ring 370 each may be an array of parts or a single monolithic structure. The movement of the actuating piston 346 is by one or more springs 380 (For example, disc springs), which are inside the drum 342 axially between the actuating piston 346 and the hub 350 are stored biased against a bias.

The locking ring 370 serves to reduce or prevent "improper engagement of the gears" by blocking the splines of the shift sleeve 348 from the engagement of the splines of the third return wheel 320 when the projections of the splines of the sliding sleeve 348 not clocked or rotatory with the splines of the third return wheel 320 are aligned. In particular, when the shift sleeve 348 through the actuating piston 346 axially to the third return wheel 320 is moved, the groove 368 in the toothed inner diameter of the sliding sleeve 348 against the balls 356 Press to the springs 354 compress and thereby an axial force against a radial surface of the locking ring 370 to apply. The axial force is an axial component of the radial force acting on the springs 354 through the engagement of the balls 356 and the curved wall of the groove 368 is exercised. The feathers 354 press the lock ring 370 against the third return wheel 320 , in particular, the conical surface of the locking ring 370 and the cog wheel cone 374 , First, there is a difference between the rotational speed of the locking ring 370 (and thus the remainder of the separation synchronizer 340 and the countershaft 306 ) and the third return wheel 320 , The spring force, the locking ring 370 along with the speed difference against the third return wheel 320 biases, generates a torque on the locking ring 370 which causes it to be relative to the hub 350 Turn slightly (eg, until the pin (s) hit the end (s) of the slot (s)) which it continues with the hub 350 rotates in the same direction. This positions the lock ring 370 in a position that the axial path of the sliding sleeve 348 with special needs. When the shift sleeve 348 Moving further, tapered tooth tips touch the ends of the splines of the contactor 348 with tapered teeth heads of the splines of the locking ring 370 , The angled tips abut each other and generate a rotational force or torque on the locking ring 370 that tend to the locking ring 370 from the way of the splines of the sliding sleeve 348 push away and release. This torque is due to the torque from the engagement of the locking ring 370 (or the friction ring 360 ) and the gear cone 374 who still turns at a different speed, resisted. If the third return wheel 320 is accelerated or decelerated to the speed of the Trennsynchronisiereinrichtung 300 coincide, the friction torque with the gear cone 374 derived to allow the splines of the sliding sleeve 348 between the splines of the locking ring 370 pass. If the third return wheel 320 not right with the locking ring 370 is clocked when the shift sleeve 348 is further moved, generates the tooth tip contact between the shift sleeve 348 and the third return wheel 320 a torque that the locking ring 370 slightly indexed (as permitted by the pin and slot connection (s)) until the splines of the sliding sleeve 348 completely into the splines of the third return wheel 320 can indent. The splines of the sliding sleeve 348 simultaneously with the splines of the sliding sleeve of the third return wheel 320 and the hub 350 together, creating the third return wheel 320 with the countershaft 306 is indented. When the pressure in the piston chamber 344 sufficiently vented, the springs are 380 the actuating piston 346 and the shift sleeve 348 return to the disengaged position where the third return wheel 320 from the countershaft 306 is disengaged.

10B shows that the actuating piston 346 directly with the sliding sleeve 348 along a locking interface that intervenes between the locking features 388 . 389 in the ring surfaces 390 . 391 of the actuating piston 346 and the shift sleeve 348 is trained. The sliding sleeve 348 is with the actuating piston 346 by overlapping radial surfaces 392 . 393 the locking features 388 . 389 connected when the ring surfaces 390 . 391 are arranged concentrically. The coupling of the locking features 388 . 389 can the shift sleeve 348 with relative rotational freedom with the actuating piston 346 connect to an angle indexing (eg 2-3 degrees) of the sliding sleeve 348 relative to the actuating piston 346 by providing a small difference (eg half a millimeter) in the radial dimensions. The radial surfaces 392 . 393 the locking features 388 . 389 are indented to one Separation of the shift sleeve 348 from the actuating piston 346 in at least one axial direction, such as during the disengaged position. The radial surfaces 392 . 393 the locking features 388 . 389 can be substantially perpendicular to the axis of rotation A of the countershaft 306 be aligned to a flat surface and a sharp corner for establishing and maintaining a contact between the actuating piston 346 and the contactor 348 during recovery. In addition, the ring surfaces 390 . 391 of the actuating piston 346 and the shift sleeve 348 adjacent to the radial surfaces 392 . 393 the locking features 388 . 389 undercut relief depressions 394 . 395 include. In various embodiments, the actuating piston 346 and the shift sleeve 348 be made of the same or different materials and using the same or different processes. The sliding sleeve 348 may be, for example, heat-treated carbonized steel and the actuating piston 346 can be a quenched and hardened forged steel without heat treatment. Furthermore, the actuating piston 346 and the shift sleeve 348 are mounted directly to each other without fasteners or other intervening components, such as by a press-fit operation, with the locking features 388 . 389 engage. As an example, the actuating piston 346 on the shift sleeve 348 are pressed, in which case the inner annular surface 390 of the actuating piston 346 the outer ring surface 391 the shift sleeve 348 overlaps and engages with it. The actuating piston 346 and the shift sleeve 348 can each have bevelled leading edges 396 . 397 include (convert the axial forces into radial forces to the actuating piston 346 to open), and the actuating piston 346 can have one or more peripheral notches 398 at the bevelled leading edge 396 its ring surface 390 to facilitate bending and to reduce stress during press-fitting operation below material yield. It should be understood that other configurations are possible and that the overlapping and coupling of components may be reversed from that described.

11 schematically shows a control hardware and a data flow for a transmission, with respect to the embodiment of the return switch device 300 can be implemented. 11A shows a control strategy for a control system 400 from 11 , When the gearbox 100 in reverse mode R, are the reverse clutch 332 and the separation synchronizer 340 engaged and the forward clutch 330 (and, if present, the countershaft brake) disengaged. When switching between the reverse mode R and the forward mode F, events may generally occur in the following order: the reverse clutch 332 is disengaged, the forward clutch 330 is engaged, the Trennsynchronisiereinrichtung 340 is disengaged (and, if present, the countershaft brake is engaged). The reverse clutch 332 and the forward clutch 330 can be engaged and disengaged at slow reverse speeds, slow forward speeds, or when the vehicle is not moving. When the transmission is in the forward mode F is the forward clutch 330 (and, if present, the countershaft brake) engaged and the reverse clutch 332 (and sometimes the separation synchronizer 340 ) disengaged. When switching between the forward mode F and the reverse mode R In general, events may occur in the following order: each countershaft brake is disengaged, the divider synchronizer 340 is engaged, the forward clutch 330 is disengaged and the reverse clutch 332 is engaged. The separation synchronizer 340 (and, if present, the countershaft brake) may be engaged and disengaged at slow forward speeds, or when the vehicle is not moving.

The tax system 400 includes a controller for a vehicle, a transmission or a return switch device 402 (or multiple controllers), which may be configured as a computer device with associated processing devices and storage architectures, hard-wired computer circuitry (or circuits), programmable circuitry, hydraulic, electrical, or electrohydraulic control, or otherwise, to various computer-based Functions and control functions in relation to the transmission 100 or the return switch device 300 perform. The control 402 and their various modules are each schematically represented by a single block. The control 402 however, their modules may include any number of processing devices that can be distributed and interconnected using various communication protocols and memory architectures. Additionally, each illustrated block may include one or more additional components than those indicated (eg, a block representing a particular clutch or synchronizer may include an associated electrohydraulic control valve). As used herein, the term module refers to any hardware, software, firmware, electronic control component, processing logic, and / or processing device, individually or in any combination, including without limitation: an application specific integrated circuit (ASIC), electronic A circuit, a processor (shared, dedicated or group processor) and a memory that executes one or more software or firmware programs, a combinatorial logic circuit and / or other suitable components that provide the described functionality.

The control 402 may be configured to receive input signals in various formats (eg, as hydraulic signals, voltage signals, power signals, etc.) and output command signals in various formats (eg, as hydraulic signals, voltage signals, current signals, mechanical motions, etc.) , The control 402 may be in electronic, hydraulic, mechanical or other connection with various other systems or devices of the vehicle, the transmission or the return switch device. The control of a work vehicle 402 For example, it may be in electronic or hydraulic communication with various power controllers, sensors, and other devices within (or outside of) the vehicle, transmission, or reverse switch device, including various timers or clocks 410 and various sensors, such as speed sensors 412 . 413 . 414 and a pressure sensor 416 for determining the absolute or relative speeds or pressures of various components of the recoil switch device 300 (eg the speed of the third return wheel 320 in terms of countershaft 306 or various components of the separation synchronizer that rotate in unison) and an operator control 418 , Various other devices and sensors (eg, temperature sensors) may be incorporated into the control system 400 be built in and from the controller 402 used to process the disclosed control logic. The various devices and sensors provide input or observation conditions to the transmission 100 or the return switch device 300 are assigned, and generate input signals or data sent to the controller 402 be transmitted. The control 402 may be onboard the vehicle or at various remote locations. The control 402 uses an input from the various devices and sensors to determine the engaged state of various components of the transmission 100 or the return switch device 300 including a drive coupling 420 , the forward clutch 330 , the reverse clutch 332 , the separating synchronizer 340 , and a parking brake or parking mode control 430 to control. The drive coupling 420 may be a clutch or a combination of multiple clutches between the engine and the output shaft 302 are arranged to control the power of the engine in one of different modes of operation of the transmission 100 to control. Various other devices (eg, a countershaft brake) may be provided by the control system 400 to be controlled.

In the illustrated embodiment, the controller includes 402 various embedded modules or submodules that process the input signals or data uniformly or collectively and output control commands for the devices of the transmission 100 or the return switch device 300 according to the control logic of the present disclosure. As can be appreciated, the modules or submodules shown may in other embodiments be combined and / or further partitioned. In particular, the exemplary control includes 402 a device control (DC) device module 440 that with the various components and devices of the transmission 100 or the return switch device 300 is connected, namely, for example, the drive clutch 420 , the forward clutch 330 , the reverse clutch 332 , the separating synchronizer 340 and parking brake or park mode control 430 , The DC module 440 communicates with a Disconnect Synchronization Engagement (DSE) module 450, which in turn communicates with one or more of a timer module 460 , a speed module 470 , a printing module 480 and a value data store 490 communicated. The DSE module 450 also communicates with a user interface (UI) module 452 that is an input from the operator control 418 receives. As shown, the timer module receives 460 Input data from the clock 410 , the speed module 470 receives sensor input data from the speed sensors 412 . 413 . 414 and the print module receives sensor input data from the pressure sensor 416 , The value data store 490 is a memory module that contains various stored values that are controlled by the controller 402 be used over one or more of its modules to execute control logic according to one or more current or sensed parameters. The value data store 490 may include one or more speed, pressure, time or other thresholds that govern the controller 402 in terms of actual or sensed parameters according to the stored control logic that may be stored in the various modules or submodules, or other on-board or remote memory modules. An exemplary control logic described by the controller will now be described 402 in terms of the gearbox 100 or the return switch device 300 is performed.

12 shows a flow chart for a control logic with which the control system 400 a method for executing a start mode or a start sequence for the transmission 100 or the Return switch device 300 implemented according to one embodiment. The start sequence is generally power to the separation synchronizer 340 and thereby apply torque to its engaging components (eg, shift collar, lock ring) to engage the third return wheel 320 to facilitate. It should be noted that the exemplary method and control logic used in relation to 12 and each of the further various figures are illustrated, may be applicable to one or more other embodiments described herein.

The boot sequence starts at step 500 in which the parking brake or park mode control 430 is engaged and all couplings (ie the drive clutch 420 , the forward clutch 330 , the reverse clutch 332 etc.) are disengaged before or during the initial commissioning of the vehicle. In the steps 502 and 504 the controller excites or pulses 402 the drive coupling 420 and the reverse clutch 332 via the DC module 440 for engagement so that power (eg torque or torque) from the power source is applied simultaneously or almost simultaneously at both the output shaft 302 as well as at the counter-wave 306 is applied. At step 506 asks the controller 402 via the timer module 460 whether the drive clutch 420 and the reverse clutch 332 are disengaged by an input from the clock 410 and a stored pulse duration value or range of values from the value data memory 490 be evaluated. In alternative embodiments, this determination may be made by using the temperature input data from temperature sensors on the input clutch 420 and the reverse clutch 332 and the stored temperature threshold or range correlated to indicate the engagement period of the clutches, rather than the use of the timer input by the controller 402 be made. In any case, the control logic will vary depending on the control 402 made provision to the steps 502 and 504 back to the drive clutch 420 and the reverse clutch 332 continue to excite, or if the pulse duration has expired, the method goes to step 508 continued, where the controller 402 the separation synchronizer 340 via the DC module 440 instructs to engage. At step 510 instructs the controller 402 the forward clutch 330 again via the DC module for engagement. At step 512 becomes the start sequence of the transmission 100 or the return switch device 300 completed according to one embodiment. In other embodiments, one or more of these steps or operations may be omitted, repeated or changed, and still achieve the desired results.

13 shows a flowchart with a control logic, with the control system 400 a method of switching between a forward mode and a reverse mode in the transmission 100 or the return switch device 300 implemented according to one embodiment. At step 520 start the procedure and at step 522 has the controller 402 via the DC module 440 previously the forward clutch 330 instructed to engage, so that the gearbox 100 in the forward mode F is. (At step 522 can the controller 402 also engage a countershaft brake if it is present.) At step 524 receives the control 402 and the operator control 418 a backward command via the UI module 452 and has the gearbox 100 or the return switch device 300 via the DC module 440 on, from the forward mode F in reverse mode R switch. (The control 402 would be a countershaft brake, if any, via the DC module 440 disengage, that of the countershaft 306 rotating.) At step 526 the control logic goes to the in 13A Subroutine shown to the Trennsynchronisiereinrichtung 340 according to an embodiment described in detail in the following paragraphs. When the separation synchronizer 340 is engaged indicates the controller 402 at step 528 the forward clutch 330 via the DC module 440 to disengage, what the output gear 312 from the output shaft 302 separates, causing the output gear 312 independent of the output shaft 302 can rotate and in this case, the countershaft rotates 306 in the to the output shaft 302 opposite direction. At step 530 instructs the controller 402 the reverse clutch 332 via the DC module 440 to engage, which is the second return wheel 318 detachable with the countershaft 306 combines. This causes the countershaft 306 in the output shaft 302 same direction based on the engagement of the first return wheel 310 that is on the output shaft 302 is stored, with an idle wheel 316 that on an idle shaft 304 is stored, and the engagement of the idle wheel 316 with the second return wheel 318 rotates. At step 532 For example, the method of switching between a forward mode and a reverse mode in a transmission reverse switch according to one embodiment is completed. In other embodiments, one or more of these steps or operations may be omitted, repeated or changed, and still achieve the desired results.

13A shows a flowchart for a subroutine for engaging the Trennsynchronisiereinrichtung 340 according to one embodiment. The illustrated control logic generally controls the engagement of the separation synchronizer 340 to the third return wheel 320 detachable with the countershaft 306 to connect and thereby the engagement of the third return wheel 320 with the driven wheel 312 to control in a controlled manner what the improper engagement of the gears or other wear on the Trennsynchronisiereinrichtung 340 and the return switch device 300 and the transmission 100 can reduce overall.

At step 540 the subprogram starts by the controller 402 via the DC module 440 and the DSE module 450 Pressure on the Trennsynchronisiereinrichtung 340 to instruct. The instructed pressure is on one in the value data memory 490 limited initial pressure value or range of pressure values that is less than the maximum pressure or another operating pressure value of the system. The control 402 can control the full initial pressure immediately. In the illustrated example, the controller 402 as by the print module 480 and the value data store 490 informed about the DC module 440 and the DSE module 450 The pressure may be linear (or possibly non-linear) over a prescribed first increase period (which may be a value or range of time or counter values stored in the value data memory 490 are stored). At step 542 asks the controller 402 as by the timer module 460 informed, the printing module 480 that is an input from the pressure sensor 416 receives and the value data store 490 , via the DSE module 450 whether the initial pressure has been reached. If not, the control logic returns to step 540 and continues to apply pressure to the separation synchronizer 340 increase until the initial pressure is reached.

At step 544. instructs the controller 402 upon reaching the initial pressure value, the pressure on the synchronizer 340 to keep it at the initial pressure value to synchronize the separation synchronizer 340 to confirm. To achieve this, the controller asks 402 at step 546 as by the speed module 470 , the speed sensors 412 . 414 and the value data store 490 informed about the DSE module 450 whether an intervention slip threshold has been reached. The engagement slip threshold may be a stored value or a range of slip values or other values (eg, speed values or ranges) that involve engagement of the separation synchronizer 340 such as speeds or one or more differential speeds across the separation synchronizer 340 , The control 402 can, as by the speed module 470 and the value data store 490 informs the slip on the Trennsynchronisiereinrichtung 340 by resolving speed input signals from the speed sensors 412 . 414 via the DSE module 450 be evaluated. The speed sensor 412 For example, the speed of the third return wheel 320 and the speed sensor 414 can the speed of the drum 342 to capture. In further embodiments, the speed sensors may 412 . 414 detect other components that arise during operation of the Trennsynchronisiereinrichtung 340 (eg the countershaft 306 or the hub 350 and the shift sleeve 348 ) at a certain point relative to each other.

When the slip, the detected speed difference on the Trennsynchronisiereinrichtung 340 is greater than the stored slip threshold, then the controller retains 402 the pressure on the Trennsynchronisiereinrichtung 340 at the initial pressure when trying to confirm the completed synchronization. In detail, the controller initiates 402 in the exemplary subroutine that is in step 548 is shown via the timer module 460 (and the clock 410 ) a timer or counter of the elapsed time since the beginning of a synchronization attempt, z. For example, the elapsed time that begins when the separation synchronizer 340 has reached the initial pressure or if the controller 402 this has determined. At step 550 ask the control 402 as by the timer module 460 (and the clock 410 ) and the value data memory 490 informed about the DSE module 450 from whether a predetermined prescribed period of time provided for the synchronization has expired. If the controller 402 determines that the step 550 is true (ie the synchronization has expired) then the control logic goes to step 554 over, where the controller 402 via the DC module 440 the parking brake or park mode module 430 to engage (and otherwise shift the transmission or vehicle to park mode). When step 550 not true, the control logic returns to step 544. back, after which the controller 402 again the synchronization (ie the engagement) of the Trennsynchronisiereinrichtung 340 reviewed.

At step 556 instructs the controller 402 when fully engaged, a final pressure for the separation synchronizer 340 via the DC module 440 at. The commanded pressure may be a maximum or further higher operating pressure value or range of pressure values stored in the value data memory 490 can be stored. The control 402 can control the full discharge pressure immediately. In the illustrated example, the controller 402 as by the print module 480 and the value data store 490 informed about the DC module 440 and the DSE module 450 The pressure may be linear (or possibly non-linear) over a prescribed final increase time period (which may be a value or range of time or counter values stored in the value data memory 490 are stored). At step 558 asks the controller 402 as by the timer module 460 informed, the printing module 480 (and the pressure sensor 416 ) and the value data memory 490 via the DSE module 450 whether the final pressure has been reached. If not, the control logic returns to step 556 and continues to apply pressure to the separation synchronizer 340 increase until the initial pressure is reached. When the final pressure has been reached, the subroutine is finished and the above-described process is at step 528 from 13 continued.

14 shows a flowchart with a control logic, with the control system 400 a method of switching between a reverse mode and a forward mode in the transmission 100 or the return switch device 300 implemented according to one embodiment. At step 560 start the procedure and at step 562 has the controller 402 previously the reverse clutch 332 and the separation synchronizer 340 via the DC module 440 instructed to engage such that the transmission 100 in the reverse mode R located. At step 564 receives the control 402 a forward command through the UI module 452 and the operator control 418 and points the gearbox 100 or the return switch device 300 via the DC module 440 on, from the reverse mode R to the forward mode F switch. At step 566 instructs the controller 402 the reverse clutch 332 via the DC module 440 to disengage, which is the second return wheel 318 from the countershaft 306 separates (or in an alternative embodiment, the first return wheel 310 from the output shaft 302 separates), what the counter-wave 306 allows to be independent of the output shaft 302 to turn. At step 568 instructs the controller 402 the forward clutch 330 via the DC module 440 to engage, which is the output gear 312 detachable with the output shaft 302 connects, which causes the output gear 312 with the output shaft 302 rotates. This causes the countershaft 306 in the output shaft 302 same direction based on the engagement of the first return wheel 310 that is on the output shaft 302 is stored, with an idle wheel 316 that on an idle shaft 304 is stored, and the engagement of the idle wheel 316 with the second return wheel 318 rotates. At step 570 the control logic goes to the in 14A and 14B subroutine, which, according to the embodiment, is described in detail in the following sections. At step 572 For example, the method of switching between a reverse mode and a forward mode in a transmission reverse switch according to one embodiment is completed. In further embodiments, one or more of these steps or operations may be omitted, repeated or changed, and still achieve the desired results, for example, the controller may 402 instruct a countershaft brake (if present) to engage to prevent the countershaft from rotating 306 to slow down or stop at certain times when in forward mode F.

14A Fig. 10 is a flowchart for a subroutine for deciding the engagement or the extraction of the separating synchronizer 340 according to one embodiment. The illustrated control logic generally controls the engagement and extraction of the separation synchronizer 340 to the third return wheel 320 detachable with the countershaft 306 to connect and thereby the engagement of the third return wheel 320 with the driven wheel 312 to control. The illustrated control logic also provides for efficient operation of the transmission or vehicle by intelligently managing the engagement state of the separation synchronizer 340 for example, the separation synchronizer 340 at certain operating conditions to achieve a fast forward / reverse shift with little or no delay and the separating synchronizer 340 under other operating conditions to reduce wear and energy consumption in connection with their intervention.

At step 540 starts the subroutine by the controller 402 , as from the speed module 470 informed about the DSE module 450 asks if the gearbox 100 or the retrace switch device operates below a prescribed first speed threshold, which may be a stored speed value or a range of values included in the value data memory 490 are stored. It should be understood that the prescribed speed threshold may correspond to one or more rotational or linear speeds that the transmission 100 or the return switch device 300 or a vehicle in which they are installed. Thus, the speed through the speed module 470 be determined, the detected speed signals from various rotary or linear speed sensor devices including the speed sensors 412 . 413 . 414 receives the speeds of various components of the transmission 100 , the return switch device 300 or other components of a vehicle in which they are installed, as well as a basic speed device of a vehicle (eg, a tachometer and the like). In either case, the sensed speed and the stored speed thresholds may be determined by the controller 402 or other controllers to correlate with a base speed value. The control logic may be useful, for example, in the subroutine shown to control the engagement state of the separation synchronizer 340 with respect to one or more basic speed values (eg relatively low Basic speed values, such as <5 km / h), and thus the following description of the exemplary control logic in at least one such context will be understood. Further, because the base speed is determined using a single sensor (eg, sensor 413 which is configured to control the speed of the output gear 312 recorded or correlated) will be referred to below and in 14A Referenced.

If the controller 402 determines that the speed is below the first speed threshold, the control logic has the engagement of the Trennsynchronisiereinrichtung 340 and does this at step 582 by first polling whether the separation synchronizer 340 currently engaged. If this is not the case, the controller rejects 402 at step 584 the engagement of the Trennsynchronisiereinrichtung 340 via the DC module 440 and the DSE module, and otherwise returns to step 580 back to retrieve the speed again. This continues until step 580 does not apply and thus pretends that the procedure of 14 the vehicle in the forward mode F controls to engage the separating synchronizer 340 at low speeds (eg <3 km / h). This prepares the return switch device 300 and effectively selects them to switch to the reverse mode R without requiring a period of zero power during the switching transition because of engagement of the separation synchronizer 340 occurs while these are outside the power flow of the transmission 100 or the return switch device 300 located.

At step 586 asks the controller 402 when the first speed threshold is exceeded, the speed with respect to a stored predetermined second speed threshold via the speed module 470 and the value data store 490 which is a higher speed value or value range or equal to this than the first speed threshold. It should be noted that the controller 402 the second speed threshold is at least partially evaluated to account for hysteresis in the sensed speed signals such that the second speed threshold may be close to (eg, 4 km / h) magnitude and provides an upper limit for the first speed threshold. In fact, in alternative embodiments of the control logic for low or negligible hysteresis applications or which do not consider hysteresis, the second speed threshold may be omitted. If the speed is below the second speed threshold, the control logic will definitely increase 582 back where the state of Trennsynchronisiereinrichtung 340 is queried and the speed is re-evaluated with respect to the first and second speed thresholds.

At step 588 asks the controller 402 at a speed above the second speed threshold again the engaged state of the Trennsynchronisiereinrichtung 340 from. When the separation synchronizer is engaged, the controller initiates 402 at step 590 a timer or counter via the timer module 460 (and the clock 410 ) of the elapsed time period above the second speed threshold. At step 592 asks the controller 402 as by the timer module 460 (and the clock 410 ) and the value data memory 490 informed about the DSE module 450 Whether a predetermined prescribed period of time (for example 30 seconds) provided for the synchronization, which corresponds to the engagement of the separating synchronizer 340 is allocated over the second speed threshold, has expired. If this is not the case, the controller asks 402 at step 594 in a similar way as in the steps 580 and 586 (ie, by comparing the sensed speed with stored speed thresholds) to determine if the speed is above a prescribed third speed threshold in the value data memory 490 stored as an assigned value or value range. The third speed threshold is higher than the second threshold and may correspond to higher speed operation (eg, 20 km / h) of the vehicle in the forward mode F. If it is less than the third speed threshold, the control logic returns to step 590 back, where the timer keeps running and the controller 402 again checked the time and speed thresholds. If the controller 402 determines that the step 588 does not apply or one of the steps 592 or 594 is true (ie, above either the time or speed thresholds), then the control logic goes to step 596 over, where the controller 402 via the DC module 440 and the DSE module 450 the separation synchronizer 340 to instruct to disengage. The subroutine is terminated and the procedure of 14 will be with the in 14B Subroutine shown continued.

14A FIG. 12 is a flowchart for a subroutine for determining the presence of the engagement or the extraction of the separating synchronizer. FIG 340 according to one embodiment. The control 402 asks at step 600 as by the speed module 470 , the speed sensors 412 . 414 and the value data store 490 informed about the DSE module 450 depending on whether a speed difference (or slip) on the Trennsynchronisiereinrichtung 340 consists. This can be done by evaluating the detected speed signals from the speed sensors 412 . 414 in relation to each other or by comparing them with a speed threshold difference or a slip threshold or value range in the value data memory 490 respectively. As previously described, to obtain a speed difference across the separation synchronizer 340 to determine the speed sensor 412 the speed of the third return wheel 320 and the speed sensor 414 can the speed of the drum 342 to capture. In further embodiments, the speed sensors may 412 . 414 detect other components that arise during operation of the Trennsynchronisiereinrichtung 340 (eg the countershaft 306 or the hub 350 and the shift sleeve 348 ) at a certain point relative to each other.

If at step 600 no speed difference is determined, energized and pulsed the controller 402 at step 602 temporarily the reverse clutch 332 via the DC module 440 and the DSE module 450 , which temporarily transfers energy to the separating synchronizer 340 about the countershaft 306 (temporarily quadrature the transmission) to apply torque very briefly to disengage certain components (eg, shift sleeve and gear cone) that have been inadvertently engaged. At step 604 checks the control 402 the differential speed across the Trennsynchronisiereinrichtung 340 again in the same way as in step 600 , If due to the pulsation at step 602 or for other reasons there is a speed difference and the seizure is confirmed, then the subroutine is ended and returns to step 572 in the process of 14 back, in which the method for switching between a reverse mode and a forward mode in a transmission-return switch, according to one embodiment, is completed. If this is not the case, the controller points over the DC module 440 the intervention of the parking brake or the mode 430 at.

It is understood that when the separating synchronizer 340 is disengaged, the countershaft 306 and thereby the reverse clutch 332 from the output gear 312 are separated. In this state, the differential speed becomes over the disengaged reverse clutch 332 that would have existed without this separation, along with the consequent wear caused by the various effects of air movement, gyroscopic flutter and other air resistance between the relatively rotating elements of the disengaged reverse clutch 332 away. Avoiding such effects, which may be particularly damaging if the transmission is operated beyond certain maximum design parameters (eg, when the vehicle is operated by gravity at excessive speeds), improves the operating life of the reverse clutch 332 and thus the whole gearbox 100 and the return switch device 300 ,

The control logic of the subprograms shown was related to the procedures of 13 and 14 described, with the subroutine of 13A in terms of a reverse mode R is described and the subroutine of 14A and 14B in terms of a forward mode F are described. It will be appreciated that the subroutines may be implemented in transmissions or rewind switch devices that operate in different modes or according to other methods or control logics.

Without limiting the scope, interpretation or application of the claims set forth below, a technical effect of one or more of the embodiments disclosed herein is a dual disconnect gear return switch for changing the direction of a vehicle between a forward and reverse direction. Another technical effect of one or more of the embodiments disclosed herein is a transmission return switch that reduces air movement or friction in a disengaged reverse clutch. Another technical effect of one or more of the embodiments disclosed herein is a transmission return switch that reduces the likelihood of gyroscopic flutter in the disengaged reverse clutch due to lower speeds. Another technical effect of one or more of the embodiments disclosed herein is a transmission reverse switch that may obstruct or stop counter-rotation of the reverse clutch during high forward speeds of the vehicle.

The terminology used herein is for the purpose of describing particular embodiments or applications and is not intended to limit the disclosure. As used herein, the singular forms "a" and "the" should also include the plural forms unless the context clearly dictates otherwise. It should also be understood that the use of the terms "comprising," "including," "comprising," or the like throughout this specification does not exclude the presence of indicated features, integers, steps, acts, elements, and / or other components the presence or addition of one or more further features, integers, steps, acts, elements, components, and / or groups thereof.

The reference numerals "A" and "B" used herein together with reference numbers are merely illustrative when describing multiple applications of a device.

One or more of the steps or acts in any of the methods, processes, or systems discussed herein may be omitted, repeated, or changed, and are within the scope of the present disclosure.

While the method described above describes embodiments of the present disclosure, these descriptions should not be considered in a limiting or restrictive sense. Rather, there are several variations and modifications that can be made without departing from the scope of the appended claims.

Claims (18)

The following is claimed: A transmission return switch for reversing a direction of a driven wheel carried by an output shaft, the transmission return switch comprising: a return shaft; a reverse clutch supported about the return shaft and having engaged and disengaged conditions; and a reverse disconnect synchronizer supported about the return shaft and having engaged and disengaged states; characterized in that, when the reverse clutch and the retrace separating synchronizer are in the engaged states, the return shaft rotates the driven gear in a reverse rotational direction against the rotational direction of the output shaft; and characterized in that, when the reverse disconnect synchronizer is in the disengaged state, the reverse clutch is disconnected from the output gear. Transmission return switch to Claim 1 further comprising: a first return wheel supported on the output shaft; an idle shaft including an idle gear engaged with the first return wheel; a second return wheel engaged with the idler wheel; and a third return wheel supported around the return shaft and engaged with the output gear, the third return wheel connected to the return shaft when the reverse disconnect synchronizer is in the engaged state; characterized in that, when the reverse clutch and the retrace separating synchronizer are in the engaged states, the return shaft rotates relative to the output shaft based on the ratios of the first return wheel to the idle wheel and the idler gear to the second return wheel and the output gear is relatively stationary to the return shaft based on a ratio of the third return wheel to the driven wheel rotates. Transmission return switch to Claim 2 characterized in that the reverse clutch releasably connects the second return wheel to the return shaft in the engaged state, and the reverse slip synchronizer connects the reverse clutch to the first return wheel in the engaged state releasably connected to the output shaft. Transmission return switch to Claim 1 , further comprising: a forward clutch supported about the output shaft and having engaged and disengaged conditions, the forward clutch releasably connecting the output gear to the output shaft in the engaged state; characterized in that, in a forward mode in which the reverse clutch is in the disengaged state and the forward clutch is in the engaged state, the output gear rotates in the rotational direction of the output shaft. Transmission return switch to Claim 4 characterized in that the forward mode further comprises the reverse clutch in the disengaged state and the reverse discrete synchronizer in the engaged state below at least one speed threshold and a time threshold and in the disengaged state above at least one speed threshold and a time threshold. Transmission return switch according to one of Claims 1 to 5 , characterized in that the return separation synchronizer is a fork-free hydraulic synchronizer. Transmission return switch to Claim 6 characterized in that the return separation synchronizer comprises a hub which is journaled about the return shaft and defines a piston space in which fluid pressure drives an actuating piston to move a shift collar. Transmission return switch to Claim 6 further comprising: a shift sleeve and a spring; characterized in that the actuating piston moves the shift sleeve in a direction along an axis of rotation of the return shaft; and characterized in that the spring biases the actuating piston to move the shift sleeve in a direction opposite to the direction in which the hydraulic fluid drives the actuating piston. Transmission return switch to Claim 7 characterized in that the retrace separating synchronizer is a half synchronizer comprising a single actuating piston and a single shift sleeve which is moved by the actuating piston in at least one direction along the axis of rotation of the return shaft. Transmission return switch according to one of Claims 1 to 9 characterized in that the retrace separating synchronizer comprises an actuating piston which moves a shift collar in at least one axial direction of the transmission retrace switch; characterized in that the actuating piston has a first annular surface with a first locking feature; characterized in that the shift collar has a second annular surface with a second locking feature configured to engage the first locking feature of the actuating piston; and characterized in that the shift sleeve is connected to the actuating piston by overlapping radial surfaces of the first and second locking features when the first and second annular surfaces are concentrically arranged. Transmission return switch to Claim 10 characterized in that the coupling of the first and second locking features connects the shift sleeve and the actuating piston with relative rotational freedom. Transmission return switch to Claim 10 characterized in that in at least one state of the transmission return switch, the radial surfaces of the first and second locking features are engaged to prevent separation of the sliding sleeve from the actuating piston in at least one axial direction. Transmission return switch to Claim 10 , characterized in that the radial surfaces are aligned substantially perpendicular to the return shaft. Transmission return switch to Claim 10 characterized in that the first and second annular surfaces include respective first and second undercut recesses adjacent the radial surfaces of the first and second locking features; and characterized in that the first and second annular surfaces include respective first and second bevelled leading edges facing the other first and second annular surfaces. Transmission return switch to Claim 10 , characterized in that the actuating piston of a first material and the shift sleeve consists of a second material which is different from the first material. Transmission return switch to Claim 10 , characterized in that the first and second locking features are coupled by a press-fitting operation of the annular piston on the shift sleeve. Transmission return switch to Claim 10 , characterized in that the annular piston comprises one or more peripheral notches on a leading edge of the first annular surface.

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