SE441512B - Hydrodynamic transmission - Google Patents

Abstract

The invention refers to a hydro-mechanic transmission with a power pack for powering a vehicle comprised of a torque conversion component (C), a connected gear box component (F) containing a pressure medium pump system as well as a component (J, K, L) with an automatic and a manual regulating device, at which the transmission and not only the individual components are used in order to produce an optimal effect without even optimising a combination effect of the individual components.<IMAGE>

Description

7906728-6 the holdings should be able to be set automatically according to a specific needs for the vehicle and its use. An additional purpose with a future transmission must be to reduce the requirement high quality and expensive materials and to reduce both the size of the mission as its service needs while increasing possible faultless operation time of the vehicle.

The situation today is that automatic transmissions are normal have higher fuel consumption per tonne of mile transport than manual electronically regulated synchronized transmissions. The situation is also that increased vehicle power has reduced the life of both the engine and transmission as well as increased service needs. In general, they are currently used transmissions are only suitable for a certain limited area of use, or it is left to the driver's opportunity to influence_fuel consumption and the utilization of different performance factors.

It is therefore an object of the invention to improve and expand the performance of a hydromechanical transmission. The purpose is more specifically to expand performance with a combination effect for the torque converter and the connected gearbox for braking goals and to improve performance both in terms of efficiency and the construction during the gears by using components with certain individual characteristics, which together create a combination effect, which improves overall performance. the invention also intends to provide a complete device, which allows a programming of an automatic system while taking account of special driving conditions such as the relationship between the weight of the vehicle and the setting of the engine and more specifically so allowing this to affect the transmission setting.

The main effect is achieved through the interrelationship between the performance of the components as will be described in the following.

The invention also intends to allow a selection of specific features per of the components to reduce the size and weight of transmission and to simplify its construction so that it can be better adapted to different purposes and to reduce the cost for a high-performance power pack of the transmission type that advantageously used for heavy buses in urban traffic and for TIR trucks and trucks. 7906728-6 In general, the invention relates to an automatic hydromechanical transmission built of special components, where the special benefits of these specific components provide the desired total capacity as well as it wanted the ability to vary performance according to requirements. The components can considered as individual parts both from a service point of view and with regard to to the possibility of varying the components within the main device for adaptation of the transmission to special needs. The transmission has one regulatory system, which can be programmed to meet the specifics the needs of the type of vehicle in question as well as the user's individual dual requirements. The transmission not only meets the desired driving performance but also a desired braking ability in that the transmission is used as part of what can be called the power package.

In more detail, the invention relates to a power package for driving one vehicle and consisting of an engine with a torque converter component, one in addition connected gearbox, a component containing a pump system for feed the liquid, a component containing a valve system and a component containing holding an automatic and a manual control device.

The invention is characterized by the following: A. The torque converter component contains in a known manner at least a pump means, at least one guide rail means and, at least one turbine means with a first ring of turbine blades arranged after the pump means, and a second ring of turbine blades arranged before the pump means a holding coupling and a friction brake to enable a locking of the hinge member against rotation; B. The connected gearbox component consists in a known manner of a servo motor-controlled multi-stage gear of a step-switching type with a planetary gear holders with a plurality of planet gears which provide a plurality of gear steps; C. The print media pump system is servomotor controlled and contains one variable capacity pump, a high pressure pump dependent on this pump and a heat exchanger; D. The valve system contains a disc valve arranged for regulating the pressure medium flow through the torque converter and through the heat exchanger at a first and / or second pressure level, the valves being arranged to open and closing gates with a relatively large area under relatively small valve movements and a second valve system for regulating the flow of pressure medium to the closed gearbox servomotors at a second and third pressure level and with the valves in the valve device arranged to open and close doors . ..- uu -... a ........... i .. 7906728-6 relatively large area through relatively small valve movements; E. The automatic control means contains a microcomputer for data processing of input signals depending on the "primary speed", the output shaft speed "and" fuel injection settings "in according to pre-programmed memories and according to manual settings so that one (selected) or more of the following conditions are met: a) output signals determine the function of components A, B, C or D; so as to obtain hydraulic drive at accelerations above a predetermined one level and below a predetermined speed on the output shaft; b) the pressure medium pump system is affected to a high capacity and pressure level below a certain speed ratio in the torque converter and below gears and hydraulic braking; D c) the pressure medium pump system is affected to a low capacity and pressure level under all other operating conditions, and d) the connected gearbox and torque converter are affected when the the control is set for braking according to the braking requirement and speed the conditions.

The use of a friction coupling connected to the guide rail member serves to allow a modulation of the vehicle's braking. Because further friction coupling is connected to the guide rail member, the guide rail can be locked against rotation and is allowed to rotate, respectively, the connected gear the box with small losses during the changes.

The device with the feed liquid system makes it possible to obtain a high efficiency in the transmission during long runs and fast gears with good cooling. In addition, the use of disc valves allows not only fast gears but also an excellent regulation of the gears.

The automatic and manual control component makes it possible for the driver not only to use the best individual components in the power package but also the best combination effect of the components below successful operating conditions and braking through both manual and automatic regulation. For closer 7906728-6 details of the various components are referred to the descriptions in the following British patents, viz During shifts in the connected gearbox, a driver can set the torque converter for high capacity, so that you get soft shifts. Because the capacity of the torque converter is adjustable by manual and automatic control can the pressure level through a different view of the issue is regulated so that capacity is high when the gear transmits high torque, while the capacity as well the torque is low during the shifting operations. Below maximum braking, for example, a high cooling capacity is achieved by setting of the feed liquid pump to maximum capacity. For brake At different levels, not only the pump capacity can be varied but if so, the motor, torque converter and gear unit are also needed nignarna. As far as the torque converter is concerned, you get a high torque ratio by setting the pump to high capacity, ie high pressure, which also results in a heat exchange with good 'cooling.

The invention will now be described in more detail with respect to selected embodiments. In the following description, figure_ 1 is a longitudinal section through a transmission according to the invention Figure 2 is a schematic diagram of the essential components. to the device in Figure 1 together with certain mechanical and regulatory bodies for these. Figures 3 and 4 are diagrams, which shows selected working characteristics of the transmission. Especially Figure 3 shows a diagram of the maximum power development / traction, and Figure 4 shows the braking force obtained at different speeds. “/ 1 In the left part of figure 1 a torque converter TC is shown consisting of a rotatable housing 2 arranged to be driven by the device's motor or similar via stop 2a. The torque converter TC has a pump member 3 with a ring of pump vanes 4, a turbine member 5 with a ring of turbine blades 6, 6 'and a rail member 7 with a ring guide vanes 8. The guide rail member 7 can be used as a turbine.

A hub 14 is connected to the turbine 5, the outer periphery of which is seen with a friction disc 12, The rotatable housing 2 contains an inwardly directed projection 2b arranged between the friction disc 12 and pump 3, and on the outside of the friction side 12 there is a servomotor 7906728-6 piston 10. The torque converter TC is of the type described in it U.S. Patent No. 3,893,551, which has a decoupling device bare pump organ. The pump member 3 is slidable to the left for insertion. grip with the rotatable housing via a friction coupling 9, which provides hydraulic operation. When the pump member 3 is moved to the right the friction clutch is released and the servomotor piston 10 is thus actuated that the friction disc 12 is pressed into frictional engagement with the committee 2b, which provides direct drive between the rotatable housing and the turbine means 5. The turbine means 5 and the hub 14 are in drive grip with the turbine shaft 16. The guide rail member 7 is mounted on a guide rail shaft 18, which rotates relative to the turbine shaft 16, and which is mounted on bearing 20. The guide shaft 18 is via one hubs and friction discs connected to a brake 26, which can be applied operated by a servo piston 23, which holds the guide rail member 7 stationary. nourished, which achieves "single rotation". The guide shaft 18 is vi- connected to a planetary gear 22, the holder of which is connected with friction discs, which form part of a brake 24, which can be applied is actuated by a servo piston 25, the guide rail member 7 rotating in opposite set direction towards the turbine means 5, which gives so-called "double rotation ". In hydraulic operation, the torque increase is achieved via the rail vanes 8 and the output of the increased torque are obtained via, the turbine member 5 to the turbine shaft 16. "Double rotation" provides occurs when the brake 24 is actuated, and this gives a much higher torque torque multiplication but over a smaller range of speed conditions than the single rotation, which is achieved by the influence of brake 23, the speed ratio being defined as the speed the ratio of the turbine shaft to the rotatable housing. Twist- the torque increase decreases with increasing speed until it becomes suitable to disconnect the hydraulic drive, ie to loosen the friction the coupling or coupling 9 and to actuate the servo piston 10 to effect drive of the trubine shaft 16 directly therefrom rotatable housing 2 via the friction disc 12 and the hub 14.

The torque converter contains a heat exchanger 68, through which The hydraulic fluid is pumped by a gear 70 via an intermediate stream gear 72. A torque converter with a heat exchanger of this type and with a pump and applicable liquid lines are described in patent U.S. Patent Nos. 4,056,019 and 4,058,980. . .-._ ..._ - _- ,. _..___.._. » 7906728-6 In order to be able to achieve an overspeed on the turbine there is a mechanical gearbox downstream of the torque converter standing of a first part P with four forward gears and a reverse gear and a second part R, which is referred to as "area switch", and which either provides a 1: 1 drive or an additional gear reduction. Such a device is described in U.S. Pat The turbine shaft 16 is connected to an annular gear 30.

The secondary or output shaft of the first gear unit P designated 32. The ring gear 30 drives a planetary gear 34 with a a plurality of gear sections consisting of a gear section 31 of large size diameter, which is mounted on a gear section by splines 33 of medium diameter, with a gear section 35 of small diameter meters to the right. Between the gear sections 33 and 35 there is a provides for mounting the planetary gear 34. The gear sections 31, 33 and 35 is in driving grip with splines on the sun wheels 36 and 38 respectively respectively 40. The gear section 35 further engages with one ring gear 50, which acts as a reverse gear. Solhjulen 36, 38 and 40 are either disengaged for free rotation or connected to the stationary part of the rotatable housing via the friction brakes 46 and 44 and 42, respectively, which are arranged to operated by servomotor pistons 47 and 45 and 43, respectively. the gear 50 can optionally be connected to the housing via a friction brake 52, which is actuated by a servomotor piston 53.

Alternatively, the ring gear 30 can be connected directly to the holder. on the planetary gear 34 and thereby directly to the secondary shaft 32 for switching on by means of a friction clutch 48, which is actuated by a servomotor piston 49, which in turn drives a rod 51a to the left so that it thereby turns a lever 51b so that its outer parts are displaced to the right, whereby the coupling 48 is switched on.

The shaft 32 in Figure 1 extends to the right into the second gear part R ("area switch"), where it is in driving engagement with a elongated splines-provided sleeve 54, which is in driving engagement partly with a hub 56 and with a planetary gear 64. The holder 60 to the planetary gear 64 is in driving engagement with a secondary gear 58, which forms the output shaft throughout the transmission. Planet- VäX @ 1H 54 is actuated by a ring gear 66, which can be braked in holding to the stationary part of the housing by means of a friction brake 67, which is actuated by a servomotor piston 69. This order allows a speed reduction between the shafts 32 and 58. - ~~ - »- ~ - -v. ~ -M- ~ .. , _, »:. fl - 7906728-6 Alternatively, the shafts 32 and 58 may be coupled together via the hub 56 and a friction clutch 62, which by friction connects the hub 56 to the planetary gear holder 60. The friction brake sen 62 is actuated by a servomotor piston 63, which acts via a lever system 65.

In the schematic diagram in Figure 2, the different ones are denoted the components in alphabetical order with the letters A up to and including K, and they will be briefly described below.

A. The primary drive means, eg a diesel engine; B 'A vehicle transmission consisting of the following elements; C. A torque converter containing a holding coupling; D A three- or four-stage planetary gear; E. An area switch; F. A system for creating fluid under pressure for lubrication cooling, actuation and actuation of clutches and brakes; G. A first valve system for distributing the pressure fluid f to the torque converter clutch and brakes; in H. A second valve system for regulating servomotors and brakes in the gearbox parts (D and E); , J. A remote control system and automatic control system for engine and transmission control: E K. A servomotor device for adjusting the setting; the engine in accordance with the control systems of J, and L. A servomotor device for adjusting the setting of a compression brake throttle.

C. The torque converter should preferably have an input torque characteristics which increase with the engine speed within an area from- "stall" up to the switching point, and when direct operation engaged, the engine speed is adjusted to suit the output walking speed. The torque converter is suitably also designed that it allows torque absorption in the turbine when it runs at overspeed, and a regulation of torque absorption achieved by modulating the engine speed.

D. Preferably, the multi-stage gear has only one planetary gear which forms the output shaft of the gear unit and a plurality planetary gears, each of which has a plurality of engaged gears. wheel sections and where each section contains one or two ring gear. 7906728-6 E. The range switch has a gear ratio between the direct operation and the lowest gear ratio, whereby the since the gear ratio in the range gear is greater than the total speak the gear ratio in the first gear.

F. The feed liquid pumping device supplies liquid pressure to the torque converter and to the servomotor-actuated clutches the brakes and / or brakes of the transmission, and it consists of a first low pressure fluid pump, which is actuated by a single impulse, so that it gives two different circulating amounts of liquid in those to the rotational speed and a number of different fluid pressure levels depending on the volume delivered, and it contains a second pump too high pressure, which is fed with liquid from the low pressure pump.

G. H. The first and second valve systems consist of one a plurality of servomotor actuated disc valves, which are arranged to quickly open and close fluid connections to electrohydraulics valves for regulating the function of the transmission. The sealing surfaces, at the servomotor actuated disc valves are designed so that they I not subject to any wear, thereby reducing fluid leakage, and the system contains means for effecting a ratio J between the pressure of the low pressure oil, which affects the valves and the pressure of the high pressure oil which affects the servomotors for the and the couplings. Q J. The automatic remote control system contains a nor- Û grind manual setting device and sensor to initialize primary pulses, which are used to determine the output signals, which according to predetermined criteria regulate the transmission function in accordance with the driving conditions.

The combination of the above components according to the invention provides an increased average speed of the vehicle, a safer driving of the vehicle and a lower fuel consumption in in relation to the number of tonne-miles, transport and average tighet. An additional advantage is the relatively small dimension and the low weight of the vehicle transmission for a certain size on the engine, which reduces costs and increases the possibility of the adaptation of the transmission. It is therefore possible to take advantage of a high performance transmission in an accessible space, and moreover, it is not the driver but the autopilot who provides one maximum utilization of the engine and choice of best driving range, so that thereby reducing fuel consumption. Since further trans- 7906728-6 10 The Commission itself has extremely low so-called speed-dependent luster saves it power. At the same time, the possibility of clean to manually control the transmission. when determining a special setting for the transmission the automatic control system not only takes into account the normal conditions but also, in contrast to previously known automatic control system, vehicle load, driving conditions uphill and setting the braking to a "level" or intensity, which is independent of or related to donet speed. "' The transmission contains eight forward gears as shown schematically and numerically in Figure 3. The first four gear steps I-IV are the steps obtained when the brake 67 in the mechanical range the gear unit is connected to the stationary housing, whereby you get one reduction of the gear ratio by the mechanical transmission sionen. The following four gear stages V-VIII constitute the same four gear stages through the mechanical transmission, but in this case the input on the mechanical range switch connected directly to the output the shaft 58 by applying the brake 62.

If the accelerator pedal is maximally depressed, you get a traction force, which is illustrated in Figure 3 with the curve Phl. Normally, however, time the vehicle accelerates faster than with the engine at the low and therefore this high traction is not obtained other than at driving up very steep slopes. If, however, the vehicle has accelerated to a certain point in relation to the engine speed the guide rail member 7 is disconnected from the turbine and connected to it stationary housing, which means that the brake 24 is released and the brake 26 is affected, which of course provides a normal single-rotary operation. This state continues until a point is reached, when direct operation is required, at which point the coupling 9 is disengaged, the member 3 is released from the rotating housing and the servomotor piston 10 is actuated for coupling the friction disc 12 to the projection 2b to the rotating housing 2. The point at which a transition takes place from one operating relationship to another is related to accelerator pedal position, which will occur at different speed relations between the pump means and the turbine means after the device accelerated sufficiently. In first gear, the vehicle can now accelerate up to about 12 km / h, and the traction 7906728-6 11 centered at maximum throttle in Figure 3 by the curve Pdll. Normally the first two or three gear stages of the mechanical transport the Commission only for starting in difficult conditions or for driving more or less fully loaded. Normally, therefore, the system is already engaged up to the fifth gear or even up to the eighth gear in any type of braking or deceleration is needed.

In conventional hydraulic braking in the torque converter direct operation is connected and the guide rail member 7 is held against the the enclosure housing, or at lower vehicle speeds, the gear is connected to the turbine by means of the brake (likewise with direct drive connected) so that the guide rail will rotate backwards. Although this conventional type of braking is satisfactory does not allow the regulation or modulation of the braking except by connecting different gears. In accordance with it is possible to achieve hydraulic braking through running the turbine at top speed and with direct operation from- I connected. with this device, the automatic control the device a gear for some overrotation of the turbine as shown schematically in Figure 4. In Figure 4, the lines mark marked n2I-VII I_VII marks it turbine speeds, and the areas marked P possible deceleration or braking force, the lower ones; the limits of the deceleration force obtained are obtained with coupled guide rail and with the motor driven depending on the torque which is transferred from the turbine to the pump.

Figure 4 shows seven brake fields, which are obtained with eight gear stages. When using four gear stages, three are obtained pieces corresponding to the brake field.

Claims (9)

7906728-6 12 P a t e n t k r a v Hydrodynamic transmission with a power pack for driving a vehicle, consisting of a torque converter (C), a gear unit connected to it (D, E), a component (F) containing a pump system for feed fluid, a component (H) containing a valve system and a component (J, K, L) containing an automatic and a manual control unit, characterized in that 7 A. The torque converter component (C) contains in a known manner at least one pump means (3), at least one guide rail means (7 ) and, at least one turbine means (5) with a first ring of turbine blades (6) arranged after the pump means (3), and a second ring of turbine blades (6) arranged before the pump means (J) a holding clutch (10, 12) and a friction brake (26) to enable locking of the guide rail member (7) against rotation; B. The connected gearbox component (D) consists in a known manner of a servomotor-controlled multi-stage gear (34) of a step changeover type with a planetary gear holder with a plurality of planet gears (31, 33, 35) which provide a plurality of gear stages; C. The pressure medium pump system (F) is servomotor controlled and contains a variable capacity pump, a high pressure pump dependent on this pump and a heat exchanger (68); D. The valve system contains a disc valve arranged for regulating the pressure medium flow through the torque converter and through the heat exchanger at a first and / or second pressure level, the valves being arranged to open and close ports with relatively large area during relatively small valve movements and a second valve system for regulating pressure medium flow to the servomotors of the connected gearbox (23, 25, 43, 45, 47, 49, 53, 63, 69) at a second and third pressure level and with the valves in the valve device arranged to open and close doors with a relatively large area through 7906728-6 13 relatively small ventiir tubes; E. The automatic control means comprises a microcomputer for data processing of input signals depending on the "primary speed", "the speed of the outgoing axis (58)" and the "fuel injection settings" in accordance with pre-programmed memories and in agreement with manual settings, so that t) e11er several of the following conditions invent a) output signals determine the function of components A, B, C or D, so that hydraulic operation is obtained at accelerations above a predetermined level and below a predetermined speed on the output axisin (58); b) the pressure medium pump system is affected; to a high capacity and pressure level during a certain speed ratio in the torque converter and during shifts and during hydraulic braking; according to the braking requirement and speed sförhåiiandena. Hydromechanical transmission according to claim 1, characterized in that it contains a two-stage growth with an exchange as an area growth. Hydromechanical transmission according to claim 1 or 2, characterized in that the automatic control means consists of means for setting the "motor fuel injection" during changes and during braking. Hydromechanical transmission according to one of the preceding claims, characterized in that the servomotors of the attached plant are of the non-rotating type, and in that the high-pressure pump can therefore have a relatively small capacity. Hydromechanical transmission according to one of the preceding claims, characterized in that the pump means (3) in the torque converter (C) can be disengaged. Hydromechanical transmission according to one of the preceding claims, characterized in that the valves are of such a type of disc type. Hydromechanical transmission according to one of the preceding claims, characterized in that all valves are actuated by servomotors and in that the servomotors are controlled by electrohydraulic valves. Hydromechanical transmission according to one of the preceding claims, characterized in that the remote control unit comprises means for controlling hydraulic braking, which in connection with the automatic control means set the torque converter, the connected gear and the motor in relation to the vehicle's driving speed and braking speed. at different levels. Hydromechanical transmission according to one of the preceding claims, characterized in that the pressure medium pump consists of two low-pressure pumps of different capacities and a high-pressure pump, the low-pressure low-pressure pump being designed with a connected bypass line and can be disconnected via a servomotor valve and a non-return valve, and where the servomotor actuated valve is in turn actuated by an electro-hydraulic valve.