Hydraulic control system for automatic gearbox with torque converter control subsystem with three power transfer paths

FIELD: transport.

SUBSTANCE: proposed system comprises first source of pressurised hydraulic fluid source to produce first fluid flow and second source of pressurised hydraulic fluid source to produce second fluid flow, and torque converter control subsystem to control said converter and its coupling. Said subsystem comprises torque converter control valve and solenoid. Said solenoid is multiplexed to aforesaid control vale and coupling. Said control valve controls hydraulic fluid flow to torque converter and other subsystems in hydraulic control system.

EFFECT: higher efficiency and response in control, smooth control.

10 cl, 6 dwg

 

The technical field

The invention relates to a control system for automatic transmission and, in particular, to an electro-hydraulic control system having a control subsystem torque Converter with three transmission routes.

The level of technology

A typical automatic transmission includes a hydraulic control system, which is used for cooling and lubrication of components in the gearbox and to actuate multiple devices transmit torque. These devices transmit torque, for example, can be friction clutches and brakes are done with gears or torque Converter. Conventional hydraulic control system generally includes a main pump which delivers fluid under pressure, such as oil, in many valves and solenoids in the valve Assembly. The main pump is driven by the vehicle engine. Valves and solenoids made with the possibility of the direction of hydraulic fluid under pressure circuit of the hydraulic fluid to the various subsystems, including engine lubrication, engine radiator, engine clutch of the torque Converter and subsystem actuators switching, which include Executive m the mechanisms, which enter into engagement device transmit torque. Hydraulic fluid under pressure supplied to the actuators of the switch, is used to introduce or withdraw from the engagement devices transmit torque to obtain different gear ratios.

Although previous hydraulic control systems are suitable for their intended purpose, there is, essentially, a constant need for new and improved configurations of the hydraulic control system in transmissions, which have improved performance characteristics, particularly from the point of view of efficiency, responsiveness and smoothness. Therefore, there is a need for a hydraulic control system that controls the lockup clutch of the torque Converter, at the same time maintaining the pressure of the hydraulic fluid in the torque Converter that is efficient and economical.

Brief description of the invention

According to the invention created a hydraulic control system for a transmission. The hydraulic control system includes a first source of hydraulic fluid under pressure for providing a first flow of hydraulic fluid, a second source of hydraulic fluid under pressure to ensure the second is Otok hydraulic fluid and the control subsystem torque Converter to control the torque Converter and torque Converter clutch. Control subsystem torque Converter includes a control valve torque Converter and solenoid. The solenoid is multiplexed on the control valve torque Converter and clutch of the torque Converter. Control valve torque Converter is arranged to control the flow of hydraulic fluid to the torque Converter and other subsystems of the hydraulic control system.

Other characteristics, aspects and advantages of the present invention will become apparent after reading the following description of the invention given with reference to the drawings, in which identical reference positions denoted by identical components, elements or features.

Brief description of drawings

Drawings, described in this document are intended only for illustration purposes and are in no way intended to limit the scope of the present disclosure. In the drawings:

figa-1D is a schematic of the hydraulic control system according to the principles of the present invention;

figa diagram of part of the hydraulic control system in the first state according to the principles of the present invention; and

figv diagram of part of the hydraulic control system in the second state according to the principles of the present invention.

Detailed description of the invention

On figa-1D hydraulic the process control system according to the present invention is indicated in General, the reference position 100. The hydraulic system 100 is a control with the ability to control the mechanisms of transmission of torque, such as synchronizers, clutches and brakes in the transmission, as well as provide lubrication and cooling of the components in the gearbox and control torque Converter connected to the gearbox. The hydraulic system 100 includes multiple interconnected or hydraulically interconnected subsystems, including subsystem 102 of the pressure regulator subsystem 104 control torque Converter, subsystem 106 flow radiator subsystem 108 control lubricant subsystem 110 managing electronic range select gearbox (ETRS) and subsystem 112 clutch.

As shown in figa, subsystem 102 of the pressure regulator is configured to provide and regulate hydraulic fluid 113 under pressure, such as oil in the hydraulic system 100 controls. Subsystem 102 pressure regulator draws hydraulic fluid 113 of the pallet 114. The pallet 114 represents a tank or reservoir, located preferably at the bottom of the transmission housing, in which the hydraulic fluid 113 is returned to and collected from the various components and areas of the transmission. Hydraulic fluid 113 in the W from the tray 114 and is passed through the filter 116 of the tray and through the hydraulic system 100 control using pump 118. The pump 118 is driven preferably by a motor (not shown) and may represent, for example, gear pump, vane pump, screw pump, or any other positive displacement pump. The pump 118 includes an inlet window 120 and the outlet port 122. The inlet box 120 communicates with the sump 114 through the liquid pipe 124. The outlet box 122 transmits hydraulic fluid 113 under pressure in liquid tubing 126. Liquid tubing 126 is in communication with a spring-loaded one-way valve 128, a spring-loaded drain safety valve 130 and valve 132 of the pressure regulator. One-way valve 128 is used to selectively prevent hydraulic flow to the main pump 118, when the main pump 118 is not working. The relief valve 130 is set at a relatively high set pressure and if the pressure of the hydraulic fluid in the liquid line 126 exceeds this pressure, one-way valve 128 immediately opens to relieve and reduce the pressure of the hydraulic fluid.

Valve node 132 of the pressure regulator includes a window 132A-G. Box 132A is in communication with liquid pipeline 126. Window W is an exhaust port that communicates with the sump 114. Window S is in communication with the liquid pipes of the wire 134, which communicates with the liquid pipeline 124 (i.e. feeds back into the intake box 120 pump 118). Window 132D is in communication with liquid pipeline 126. Liquid window A is in communication with the liquid pipe 136 and through the hole 138 limit the flow of liquid pipeline 140. Liquid window 132F is in communication with liquid pipeline 140. Liquid pipeline 140 is divided into at least two parallel branches 140A and 140V, and each has spaced holes in it or strip A and V limit the flow of different sizes, respectively, as shown in figv. Finally, the window 132G is in communication with the liquid pipe 142.

Valve node 132 of the pressure regulator additionally comprises a valve 144, located slidable in the channel 146. The valve 144 automatically changes position to reset the excess flow from the fluid line 126 until then, until it reaches the equalization of pressure between the set pressure and actual pressure. The valve 144 is regulated by the solenoid 148 variable drain which communicates with the liquid pipe 142. For example, the solenoid 148 sets the pressure fluid through the supply of hydraulic fluid under pressure in the box 132G for influencing the valve 144. Simultaneously press the s fluid from the fluid line 126 enters the window 132A and the effect on the opposite side of the valve 144. The alignment between the pressure set by the pressure from the solenoid 148 and the pressure in the pipe 126 is achieved when the valve 144 is moved and makes possible selective communication between the window 132D and window S, whereby venting pressure from the fluid line 126.

Liquid tubing 126 is also reported lower flow valve block 132 of the pressure regulator with the one-way valve 150. One-way valve 150 provides fluid communication from the fluid line 126 to the fluid line 152 and prevents fluid communication from the fluid line 152 to the fluid line 126. Liquid tubing 152 is communicated with the valve node 154 flow limitation.

Valve node 154 flow limitation limits the maximum pressure of the hydraulic fluid subsystem 104 control torque Converter, subsystem 106 management radiator, and various solenoids control, as described below. Valve node 154 limited supply includes window 154A-F. Open S and 154F are in communication with the liquid pipe 136 and therefore the window A valve 132 of the pressure regulator. Window 154D is in communication with the liquid pipe 152. Open A, B and E are outlet ports that communicate with the sump 114.

Valve node 154 is ograniczenia supply additionally includes a valve 156, located slidable in the channel 158. The valve 156 automatically changes position to reduce flow from the fluid line 152 (i.e., the line pressure from the pump 118) in the liquid pipe 136. For example, the valve 156 is shifted to the first position by a spring 160. In the first position, at least a partial flow of fluid from the pipe 152 is transmitted from the window 154D through the valve node 154 flow limitation in the window S and then in liquid tubing 136. When the pressure increase in the liquid line 136, the back pressure acting on the valve 156 through the window 154F, moves the valve 156 against the action of spring 160, thereby further reducing the pressure of the hydraulic fluid in the liquid line 136, until it reaches the equalization of pressure across the valve 156. By controlling the pressure in the liquid line 136 which communicates through a valve 132 of the pressure regulator liquid pipe 140, the valve 154 limited supply and the valve 132 of the pressure regulator control the flow of pressure to the subsystem 104 controls the torque Converter lock-up (TCC) and subsystem 108 control grease.

Subsystem 102 of the pressure regulator further comprises an alternative source of hydraulic fluid, which includes an auxiliary pump 170. Supporting us is 170 preferably is driven by an electric motor, battery or other primary motor (not shown) and may represent, for example, gear pump, vane pump, screw pump, or any other positive displacement pump. Auxiliary pump 170 includes an inlet window 172 and outlet port 174. The inlet box 172 communicates with the sump 114 through the liquid pipe 176. The outlet box 174 transmits hydraulic fluid under pressure in liquid tubing 178. Liquid pipe 178 is in communication with a spring-loaded drain safety valve 180 and the one-way valve 182. Relief valve 180 is used to reduce the excess pressure in the liquid line 178 from the auxiliary pump 170. One-way valve 182 is in communication with the liquid pipe 152 and has a capability of flowing hydraulic fluid from the fluid line 178 in liquid tubing 152 and prevent the flow of hydraulic fluid from the fluid line 152 in liquid tubing 178. Therefore, under normal operating conditions to prevent back filling auxiliary pump 170 fluid flow from the pump 118 through a one-way valve 182. During the operation modes with high efficiency when the engine and therefore the pump 118 are dormant and put into Zats the district heating auxiliary pump 170, to prevent back filling pump 118 fluid flow from the auxiliary pump 170 through a one-way valve 150.

With particular reference to figv, subsystem 104 TCC receives hydraulic fluid under pressure from valve block 154 limitations of the feed liquid pipe 136 and valve block 132 of the pressure regulator for liquid pipeline 140. Subsystem 104 TCC includes valve node 184 control TCC and the solenoid 186 which regulates the pressure in the torque Converter 188. The torque Converter 188 includes a coupling A of the torque Converter. Clutch A Converter configured to direct mechanical connection of the output of the engine (not shown) to the input of a transmission (not shown).

Valve node 184 control TCC includes box 184A-M Box 184A and 184c, German are outlet ports that communicate with the sump 114. Window S communicates with the liquid pipe 189. Liquid pipeline 189 communicates with the switch 190 pressure control valve TCC. Window 184D communicates with the branch 140D fluid line 140. Branch 140D is parallel branches 140A and 140V. Window HE reported with safety drain valve 192, which produces hydraulic fluid under pressure when the clutch A Converter included is typed in the engaged position, as is described below. Window 184F communicates with the torque Converter 188 through the liquid pipe 191. Open 184G and 184L are connected with the liquid pipe 196. Liquid pipeline 196, in turn, communicates with the subsystem 106 of the heat sink. Window 184H communicates with the torque Converter 188 through the liquid pipe 193. Window 184I is in liquid communication with the liquid pipe 136 through the hole or pad 195 limitations of liquid. Every window and 184J 184K is in communication with branches 140A and 140V, respectively, through openings A and B, respectively. Finally, the window M communicates with the liquid pipe 198. Liquid pipeline 198 communicates with the solenoid 186 and with the torque Converter 188.

The solenoid 186 is a control device configured to control the flow of hydraulic fluid under pressure supplied under pressure from the fluid line 187. The solenoid 186 is preferably a solenoid is a variable force and a high flow rate, which is normally closed, although other types of control devices and actuators can be used without deviation from the scope of the present invention.

Valve node 184 control TCC additionally includes a valve 200, located slidable in the channel 202. In before agema example, the valve 200 is a spool valve, with many belts 203, located along the length of the valve 200. The belts 203 engages with the seal channel 202 and executed with the possibility, depending on the position of the valve 200, isolation and providing communication between Windows 184A-M Valve 200 is moved between at least two positions including a first position or a position to return to the original state shown in figa, and the second position or the position of the progress made, shown in figv. Bias element or spring 204 is located on the end of valve block 184 TCC and is engaged with the end face 205 of the valve 200 to move the valve 200 in a position to return to its original state. In the position of the reset window S communicates with the window 184D, window A disjoined, window 184F communicates with the window 184G, window 184H reported with Windows 184I and 184J, window 184K disjoined, and the window 184L disjoined. Window 184M remains in communication with the liquid pipe 198 and the solenoid 186.

The valve 200 is moved to the position carried out stroke when the solenoid 186 is excited or opens, and the flow of hydraulic fluid under pressure supplied from the solenoid 186 on liquid pipeline 198 in the window M. When the pressure of hydraulic fluid acting on the end face 207 of the valve 200 front end 205, rises above the threshold, the valve 200 is made, which allows the progress in the provision made progress, shown in figv. In position made progress window S communicates with the box 184c, German, window 184D disjoined, window E communicates with the window 184F, window 184G disjoined, window 184I communicates with the window 184H, window 184J disjoined, and the window 184K communicates with the window 184L.

The following describes the principle of operation of the subsystem 104 control TCC. During operation of a transmission having a hydraulic system 100 controls, where the torque Converter 188 acts as a fluid coupling between the engine and gearbox for increased torque, the hydraulic system 100 is a control with the possibility of flow of hydraulic fluid to the torque Converter 188 for cooling and lubrication of the components of the torque Converter 188. Therefore, in the first operating condition when the torque Converter 188 serves as a fluid coupling and removed from engagement of the clutch A of the torque Converter, solenoid 186 is closed. Therefore, the valve 200 valve block 184 control TCC is set to return to its original state. The flow of hydraulic fluid under pressure is passed from the valve 154 limitations of the feed liquid pipe 136 and through the opening 195 in the box, 184I. Also, the flow of hydraulic fluid under pressure supplied from the valve 132 to the control pressure liquid pipe 140 and the branch 140A through the hole A the window 184J. On the Oka hydraulic fluid are combined in and out of the valve block TCC through the window 184H. Hence the flow of hydraulic fluid under pressure supplied from the window 184H in the input 209 of the torque Converter 188 on the liquid pipe 193. Hydraulic fluid circulates in the torque Converter 188, providing cooling, lubrication and hydraulic coupling, and out through the exhaust port 211 in the torque Converter 188. The return flow of hydraulic fluid is supplied via the liquid pipe 191 in the window 184F valve node 184 TCC. The return flow of hydraulic fluid out of the valve block 184 TCC through the window 184G, which transmits the return flow of hydraulic fluid subsystem 106 of the heat sink. In addition, the flow of hydraulic fluid from the fluid line 140 is passed to the window 184D the branch 140D. The hydraulic fluid then exits the valve block 184 TCC through the window S and communicates with the sensor 190 pressure, thereby indicating the position of the valve 200, based on the pressure applied to the sensor 190 via a valve node 184 TCC.

During operation of a transmission having a hydraulic system 100 controls, where the torque Converter 188 is no longer needed as a magnifier of torque, the hydraulic system 100 is a control with the possibility of entering into engagement with the clutch A of the torque Converter, at the same time controlling the flow of hydraulic fluid subsystem 106 is of adiator. Therefore, in the second operating state, when the torque Converter 188 is not as fluid couplings, and coupling A torque Converter is put in the engaged position, opens the solenoid 186. Therefore, hydraulic fluid under pressure out of a solenoid 186 and concatenates the clutch A of the torque Converter, at the same time feeding the flow of hydraulic fluid out of the window M valve block 184 TCC. When increasing the pressure of the hydraulic fluid acting on the valve 200 from the window M through the solenoid 186, exceeded the threshold, when the valve 200 is shifted against the action of spring 204 and moves to the progress made, shown in figv. When the valve 200 is moved, hydraulic fluid from the fluid line 140 is directed along the branches 140A-IN holes A-IN, thereby controlling the flow of hydraulic fluid out of the window 184H and therefore the flow of hydraulic fluid to the torque Converter 188. In the position carried out the flow of the hydraulic fluid flow from the fluid line 140 is transmitted through the branches 140V through the hole W the window 184K. This flow of hydraulic fluid then exits through the window, 184L and communicates with the subsystem 106 of the heat sink in a liquid pipeline 196. The liquid flow through the liquid pipe 136 is passed through the opening 195 in the window 184I, which, in turn, comes out is via the window 184H and is supplied to the torque Converter 188. As the opening 195 fewer holes A, decreases the fluid flow to the torque Converter 188. The flow of hydraulic fluid out of the torque Converter 188 and is transmitted through the liquid pipe 191 in the box, 184F and from the window 184F - pressure release valve 192. Install drain valve 192 controls the maximum pressure of the hydraulic fluid in the torque Converter 188, thus allowing the torque Converter 188 to be filled with hydraulic fluid pressure, which is below the maximum pressure. In addition, the liquid pipe 189 and therefore the sensor 190 pressure, disconnect from the flow of hydraulic fluid from the fluid line 140, and the liquid pipe 189 is pumped through messages between the window S and 184c, German. This pressure drop in the liquid line 189 is determined by the sensor 190 pressure, thereby indicating the position of the valve 200, based on the pressure applied to the sensor 190 via a valve node 184 TCC.

Subsystem 106 management radiator includes oil cooler 210 and the oil filter 212 fine cleaning. Oil cooler 210 is in communication with the liquid pipe 196. Oil filter 212 is in communication with an oil cooler 210 and liquid pipeline 214. Liquid pipeline 214 includes three branches A, which are reported with p is Sistemas 108 control lubricant and fourth branch 214D, which is communicated with the spring loaded one-way valve 216. Branch S includes a hole 215 limit the flow, or the hole override used to control the flow of fluid through the subsystem 108 lubrication, as described in more detail below. One-way valve 216 is connected with the liquid pipe 189. If the pressure of the hydraulic fluid in the liquid line 214D exceeds the threshold pressure, one-way valve 216 opens immediately to drop and reduce the pressure of hydraulic fluid in the liquid line 214D. Subsystem 106 management radiator additionally includes a spring-loaded drain relief valve 218 or located parallel to the oil filter 210, or made in one piece with oil filter 210, which allows hydraulic fluid to bypass the oil filter 210 in the case of noncompliant flow radiator. A drain valve 218 is fixed to the preset pressure, and, if the pressure of the hydraulic fluid in the liquid line 196 will exceed this pressure, a drain valve 218 opens immediately for increasing the flow of hydraulic fluid from subsystem 106 flow radiator.

Subsystem 108 control grease regulates the pressure of the fluid for lubrication as f is NCLI pressure in the pipeline, supplied from the pump 118 or auxiliary pump 170. Hydraulic fluid, adjustable subsystem 108 control lubricant lubricates and cools the various moving parts of the transmission and provides a source of hydraulic fluid for filling the centrifugal expansion joint couplings. Subsystem 108 control of the lubrication takes hydraulic fluid from the subsystem 106 flow radiator for liquid pipeline 214.

Subsystem 108 control lubricant includes a valve node 220 regulator lubrication and ball check valve 221. Ball check valve 221 includes three Windows A-C. Ball check valve 221 closes the window from the Windows A and B, which gives a lower hydraulic pressure, and provides communication between the window from the Windows A and B that has or gives a higher hydraulic pressure, and an outlet window S.

Valve node 220 regulator lubrication includes window A-L. Box A communicates with the liquid pipe 126 and therefore takes the pressure from the pump 118. The window 220 communicates with the liquid pipeline 222. Liquid pipeline 222 includes two branches A and B. Branch A communicates with the subsystem 110 ETRS, and branch V communicates with the window W ball check valve 221. Open 220C and 220L are the finishing window that reports which are stated with the pallet 114. Window 220D reported with liquid pipeline A. Open E and 220H are connected with the liquid pipe 224. Liquid pipeline 224 includes a branch A, which communicates with the window A ball check valve 221. Open 220I and 220J are connected with the liquid pipe 140 and the switch 226 pressure. Finally, the window 220K communicates with the window S ball check valve 221.

Valve node 220 regulator lubrication additionally includes a valve 228, located slidable in the channel 230. Valve 228 has three functional positions: the main regulatory position, additional regulatory position and the position of the override. The valve 228 is moved between positions based on equilibrium of forces acting on each of the first end and the second end of the valve 228. The main regulatory provision provides an output pressure through the liquid pipe 224, which is proportional to the pressure (i.e. the pressure in the liquid line 126). Mainly regulating the position of the pressure liquid through the pipe 126 enters the window A and acts on the end face of the valve 228 against the bias of the spring 235. When the valve 228 performs a move against the action of the spring 235, the window 220F communicates with the window E. Consequently, the flow of hydraulic fluid from the subsystem 106 RA is iator is transferred from the fluid line W the window 220F, through the valve 228 and of the liquid window E in liquid tubing 224. Back pressure from the fluid line 224 is transmitted through the branches A, through the ball check valve 221 and the valve node 220. The hydraulic fluid acts on the valve 228 and creates a leveling force against the action of the pressure in the pipeline, which keeps the valve 228 in the position of regulating fluid flow in liquid tubing 224. In addition, Windows 220I, 220J, 220C and 220G dismantled valve 228, which, in turn, maintains the pressure of the liquid in the liquid line 140 is high, which, in turn, allows the switch 226 pressure to perceive high pressure, thereby indicating that the valve 228 regulates the liquid flow to the liquid tubing 224.

If the fluid flow from subsystem 106 of the heat sink is significantly reduced, the pressure acting on the valve 228 of the fluid line 126, moves the valve 228 in the advanced position or the position of the progress made. In the accessory position not only increases the fluid flow from subsystem 106 of the radiator by opening 220F for Windows E, but is also a window message 220I with liquid window 220H. Consequently, the flow of fluid from the valve 154 flow limitation is transmitted to the valve 220 controls the liquid lubricant to Tomo pipeline 140, thereby increasing the fluid flow in the liquid line 224. Hole 237 restricting the flow of the liquid line 140 restricts the flow of hydraulic fluid to the valve 220 controls grease.

Finally, the position of the override is achieved by actuation of solenoid 240 (see figs), which is in communication with liquid pipeline A. Position override is actuated during the low pressure in the pipeline (i.e. when the pump 118 operates at a reduced speed due to the idling of the engine). The solenoid 240 is a solenoid on/off, which is multiplexed with the subsystem 110 ETRS, as described in more detail below. The flow of hydraulic fluid from the solenoid 240, when it is enabled, is transmitted to the ball check valve 221 for liquid pipeline A. Ball check valve 221 prevents the admission of fluid flow from the solenoid 240V liquid tubing 224. When the fluid flow from the solenoid 240 is supplied in the box 220K, hydraulic fluid comes into contact with the valve 228 and, together with the spring 235 moves the valve to return to its original state. In the position of the override box 220F disjoined from the window E. However, the window 220G remains in the message window 220H. The fluid flow from subsystem 106 of the heat sink through the liquid pipes of the wire IS reduced by the relative small holes 215 override. In addition, the window 220D previously disjunct becomes communicating with window 220C. Therefore, the fluid flow from subsystem 106 of the heat sink are further reduced because the fluid flow is diverted through the branch A in 220D window, from the window 220D window 220C and from the window A in the pallet 114. Finally, the window 220J becomes communicating with window 220L, thereby allowing fluid flow from the valve 154 limiting supply of liquid through a pipe 140 to go into the sump 114. However, due to the grooves 243 gasket located in front of the direction switch 226 pressure, pressure drop between the switch 226 pressure and outlet box, 220p. The pressure drop experienced by the switch 226 pressure, confirms that the valve 228 is set to override. Position override significantly reduces the flow of hydraulic fluid in the liquid pipe 224, and therefore the components of the transmission, thereby reducing parasitic losses during the rotation. Position override is used when the conditions get of low power, such as engine idle.

The switch 226 pressure control valve lubricant and the switch 190 pressure control valve TCC interact to diagnose a stuck valve block 132 of the pressure regulator or stuck valve block 154 limiting supply. The condition is without applied pressure is set TCC position valve block 184 control TCC and position override to lubricate the valve block 220 grease. On both switches 226, 190 pressure is supplied hydraulic fluid pressure which is generated valve node 154 limiting supply. Depending on the specific condition of the valve nodes 184, 220, both switches 226, 190 pressure, indicating the absence of pressure can be used as a diagnostic signal.

The following describes the subsystem 110 control ETRS, returning to figs and with continuing reference to figa and 1B. Subsystem 110 control ETRS uses hydraulic fluid under pressure from pump 118 or auxiliary pump 170 to the liquid pipe 152 to actuate range by subsystem 112 of the actuator coupling. Subsystem 110 control ETRS controlled by hydraulic fluid from the valve block 154 control limit feed liquid pipe 136. Subsystem 110 control ETRS includes the previously described solenoid 240, as well as three additional solenoid 242, 244 and 246. Each of the solenoids 240, 242, 244, 246 is a solenoid on-off switch with normally low pressure, each of which is supplied with hydraulic fluid through a liquid pipe 136. Liquid pipeline 136 additionally supplies the hydraulic fluid to the solenoid 148 (see figa). The solenoids 240, 242, 244 and 26 are used to actuate the valve block 250 ETRS, valve block 252 fixation and first and second valve nodes 254, 256 mode.

Valve node 250 ETRS includes box 250A-H. Box 250A is connected with the liquid pipe A. Window 250V reported with liquid pipeline 260. Window S communicates with the liquid pipe 262. The 250D box communicates with the liquid pipe 152. Window E communicates with the liquid pipe 264. Window 250F communicates with the liquid pipe 266. Liquid pipeline 266 communicates with the solenoid 242. The 250G box represents one side of the outlet box, which communicates with the sump 114, which is used to improve the response time of the valve block 250 ETRS to return to its original state at the time of return to the position of "Parking" when very cold working conditions. Finally, the window 250H is an exhaust port that communicates with the sump 114.

Valve node 250 ETRS additionally includes a valve 268, located slidable in the channel 270. The valve 268 is driven in position made the move or in the "Out of place" through solenoid 240 and through the hydraulic fluid acting on the valve 268 is supplied through the liquid pipe 262, and in position to return to its original state or position "Parking" by the spring 272 or via hydraulics the second liquid, acting on the valve 268 is supplied through the liquid pipe 266. In position Outside Parking" solenoid 240 is open, and fluid from the pipeline A comes in contact with the valve 268 and moves the valve 268 against the action of the spring 272. In addition, the fluid from the pipe 262, which is fed by line pressure through valves 254 and 256 mode and the fluid line 152, comes in contact with the valve 268, through the valve stroke. In this state, the window 250D communicates with the window E. Therefore, the hydraulic fluid pressure from the fluid line 152 is passed to the window 250D, from the window 250D through the valve node 250 ETRS in the window E and from the window E - liquid pipe 264. Liquid pipeline 264 communicates with sarvotham 276 "Parking". Hydraulic fluid enters Servotel 276 "Parking". Servotel 276 "Parking lot" includes the piston 278, which moves in contact with the hydraulic fluid, thereby mechanically deriving from the gearing system "Parking lot" (not shown). The node 281 solenoids prohibition "Parking lot" connected to seriously 276 "Parking". The node 281 solenoids prohibition "Parking" is a solenoid with mechanical detent to keep the system out of the state "Parking", if the operator wants the vehicle was moving when the engine is switched off. the green solenoids 281 prohibition "Parking" also includes preferably two switch positions, one mechanical and one on the Hall effect, which confirms the position of the system "Parking" the engine controller and the controller's transmission, for use in diagnostic purposes.

In the position of "Parking" the solenoid 240 is closed and the solenoid 242 is opened, and the valve 268 is returned to its original state under the action of the spring 272 and through the hydraulic fluid supplied from the solenoid 242 pipeline 266. In this position the window HE communicates with the window 250H, and Servotel 276 "Parking" executes the release, thereby introducing into engagement system "Parking". The valve 268 is executed so that the spring 272 and the hydraulic fluid from the solenoid 242 overcome the forces acting on the valve 268, any one of the hydraulic fluid supplied to the solenoid 240, and hydraulic fluid supplied through the liquid pipe 262. If there are both a source of hydraulic fluid, the forces acting on the valve 268 hydraulic fluid from the solenoid 240 and the hydraulic liquid supplied through the liquid pipe 262, overcome the forces acting on the valve 268 spring 272 and hydraulic fluid from the solenoid 242, thus ensuring that it can be overcome faulty signal. Management "Parking" are made so that if you lost all hydraulic pressure in the hydraulic system 100 from the management, engages the system "Parking".

The first valve node 254 mode includes box 254A-K. Window A communicates with the liquid pipe 280. Window 254V communicates with the liquid pipe 282. Window S communicates with the liquid pipe 152. Window 254D communicates with the liquid pipe 284. Window E communicates with the liquid pipe 286. Open 254F and 254J are outlet ports that communicate with the sump 114. Window 254G communicates with the liquid pipe 288. Window 254H communicates with the liquid pipe 290. Window 254I communicates with the branch 137 fluid line 136. Branch 137 communicates with the solenoid 244 and liquid pipe 136 through holes 291 flow. Window 254K communicates with the liquid pipe 136 through holes 296 flow.

The first valve node 254 mode additionally includes a valve 292, located slidable in the channel 293. The valve 292 is actuated by the solenoid 244 and a spring 294. When the solenoid 244 is open, fluid from the pipe 136 is passed through the solenoid 244 and moves the valve 292 against the action of the spring 294. Therefore, the valve 292 is moved between the position made progress when the spring 294 is compressed, and status return to the original state shown in figs. Also against the spring 294 acts mukozalnogo stroke (i.e. hydraulic fluid that is used to initiate the state of the reverse), supplied in a box 254H reported through the liquid pipe 290, the second valve node 256 mode, the liquid pipe 286 and liquid tubing 284 from the valve block 250 ETRS. The valve 292 with a spring 294 is valid or oil removal from Parking lots, or the oil return to the Parking position, is passed through the liquid pipe 280 from the valve block 250 ETRS. In position made progress solenoid 244 is opened, and the liquid from the pipe 137 is in contact with the valve 292 and moves the valve 292 against the action of the spring 294. In this state, the window 254V communicates with the window 254J and performs a release window S and 254D communicate with the window A, window 254G communicates with the window 254F and executes the release, and the window 254K closed.

In the position of the reset solenoid 244 is closed, and the valve 292 is located under the action of the spring 294 and hydraulic fluid from the pipe 280. In this position the window 254V communicates with the window S, Windows E and 254D communicate with the window 254F and perform the release, and the window 254G communicates with the window 254K. Therefore, as a result of implementation progress and return to the initial state of the valve 292 hydraulic fluid in liquid pipelines 282, 288 and liquid pipeline 286.

Valve node 252 commit mainly includes window A-E. Open A and B are outlet ports that communicate with the sump 114. Window S reported with liquid pipeline 300. Window 252D communicates with the liquid pipe 280. Window HE reported with liquid pipeline 301, which, in turn, communicates with the solenoid 246. Valve node 252 fixation includes the valve 303, located slidable in the channel 305. The valve 303 is driven by a solenoid 246 and the spring 307. When the solenoid 246 is open, fluid from the pipe 136 is passed through the solenoid 246 and the pipe 301 and moves the valve 303 against the action of the spring 307. The valve 303 is moved between the position made progress when the spring 307 is compressed, shown in figs, and return to its original state when the spring 307 is not compressed. In position made progress window S communicates with the window W and executes the release, and 252D box is blocked. In the position of the reset window S communicates with the window 252D. Valve node 252 commit is made to lock or entering into engagement with the second valve node 256 mode.

Ball check valve 309 is located between the valve 250 ETRS valve 252 fixation. Ball check valve 309 includes three Windows 309A-N-Box 309A reported with liquid pipeline 260. Window W communicates with the liquid is Truboprovod 266. Window S communicates with the liquid pipe 280. Ball check valve 309 closes the window from the Windows 309A and V, which gives a lower hydraulic pressure, and provides communication between the window from the Windows 309A and V that has or gives greater hydraulic pressure, and an outlet window S.

The second valve node 256 mode includes box 256A-N. Open A, 256D, 256J and 256M are outlet ports that communicate with the sump 114. Window W reported with liquid pipeline 300. Open S and 256G communicated with liquid pipeline 302. Window E communicates with the liquid pipe 290. The 256F box communicates with the liquid pipe 286. Window 256H communicates with the liquid pipe 282. Window 256I reported with liquid pipeline 187 that powers the solenoid 186. Window 256K communicates with the liquid pipe 288. Window 256L reported with liquid pipeline 306. Window 256N reported with liquid pipeline 308.

The second valve node 256 mode additionally includes a valve 310, located slidable in the channel 312. The valve 310 is driven by a solenoid 246 through the valve 252 fixation and a spring 314 or directly through the liquid pipe 301 and the ball check valve 320. The valve 310 is moved between the state made progress when simays the spring 314, shown in figv, and return to its original state. When the solenoid 246 is open, hydraulic fluid is conveyed through the pipeline 301 on the second valve node 256 mode, and the valve node 252 fixation. The liquid is transmitted to the valve node 252 commit moves the valve 303 in his condition made progress, thereby allowing messages from the solenoids 240 and 242 to side with the valve spring 310 of the second valve block 256 mode. If any of the solenoids 240 or 242 is open (i.e. powering the status "Out of place" or return to "Park"), the hydraulic fluid is transmitted through the ball check valve 309, pipeline 280, via a valve node 252 fixation and second valve node 256 mode on the pipeline 300. This hydraulic fluid is then maintains the valve 310 in the second position. If the liquid from the solenoids 240 and 242 is not in contact with the valve 310, hydraulic fluid, coolant solenoid 246 moves the valve 310 in its state made progress.

In position made progress window S communicates with the window 256D, and executes a release window HE reported with 256F box, the box 256G locks, window 256I communicates with the window 256H, window 256J locks, window 256L reported with 256K window, and the window 256M is blocked. In the position of the return in the original condition the box S is blocked window E communicates with the window 256D, and executes a release window 256G reported with 256F box, the box 256H locks, window 256I communicates with the window 256J and executes the release, 256K window is locked and the window 256L communicates with the window 256M and performs the release.

Contour oil fixation is determined by the liquid pipe 136, liquid pipeline 288, liquid pipeline 306, a ball check valve 320 and a liquid pipeline 308. Ball check valve 320 includes three Windows 320S-s Window 320S reported with liquid pipeline 301. Window 320V reported with liquid pipeline 306. Window S reported with liquid pipeline 308. Ball check valve 320 closes the window from the Windows 320S and 320V, which gives a lower hydraulic pressure, and provides communication between the window from the Windows 320S and 320V, which has or delivers more hydraulic pressure, and an outlet window S. Oil fixation is transmitted by circuit oil fixation of the pipe 136, when the first valve node 254 mode is set to return to its original state, and the second valve node 256 mode is in position made progress. The oil is transferred from the fixing pipe 136 through the first valve node 254 mode, the pipeline 288, through the second valve node 256 mode, the pipeline 306, through the ball check valve 320 and the line is the gadfly 308 to influence the valve 310.

With reference to fig.1D and continuing reference to figs, subsystem 112 clutch delivers hydraulic fluid to the actuators 330A-E couplings. Actuators 330A-E clutches are hydraulically actuated pistons, each of which is engaged with one of the many devices transmit torque to achieve different gear ratios. The actuator A clutch includes two areas EA and 330Eb application. Each of the actuators 330A-E coupling is controlled by a solenoid 332A-F with a variable force, and the actuator A clutch is controlled by two solenoids A and 332F with a variable force. This separate control of the actuating mechanism A clutch provides maximum flexibility for configuring characteristics of the torque couplings for a wide range of conditions switch with high torque and low torque.

The solenoid 332A is in communication with the liquid pipe 334 and liquid pipe 336. Liquid pipeline 334 communicates with a ball check valve 338. Ball check valve 338 includes three Windows A-s Window A communicates with the liquid pipe 290. Window W reported with liquid pipeline 340. Window S communicates with the liquid pipes of the wire 334. Ball check valve 338 closes the window from the Windows A and B, which gives a lower hydraulic pressure, and provides communication between the window from the Windows A and B that has or gives greater hydraulic pressure, and an outlet window S. Therefore, the solenoid 332A is supplied hydraulic fluid through the valves 254, 256 mode from the fluid line 152 (i.e. through either oil the provisions of the "Movement", or oil position "reverse" and so it can be communicated to the pressure only when the valves 254, 256 mode are located in the "Movement" or "reverse"). Therefore, prevents the inadvertent inclusion of the transmission in "Neutral"if the solenoid clutch does not create high pressure. Liquid pipeline 336 supplies the hydraulic fluid from the solenoid 332A to the actuator switch 330A.

The solenoid B is in communication with liquid pipeline 340 and a liquid pipe 342. Liquid pipeline 340 communicates with a ball check valve 344. Ball check valve 344 includes three Windows A-s Window A reported with liquid pipeline 302. Window W communicates with the liquid pipe 187. Window S reported with liquid pipeline 340. Ball check valve 344 closes the window from the Windows A and B, which delivers less the e hydraulic pressure, and provides communication between the window from the Windows A and B that has or gives a higher hydraulic pressure, and an outlet window S. Therefore, the solenoid B is supplied hydraulic fluid through the valves 254, 256 mode from the fluid line 152 (i.e. by means oil the provisions of the "Movement" and therefore it can be communicated to the pressure only when the valves 254, 256 mode are set to "Motion"). Liquid pipeline 342 supplies the hydraulic fluid from the solenoid V to the actuator V switch.

The solenoid S is in communication with liquid pipeline 340 and a liquid pipe 346. To the solenoid S is supplied hydraulic fluid through the valves 254, 256 mode from the fluid line 152 (i.e. by means oil the provisions of the "Movement", so it can be communicated to the pressure only when the valves 254, 256 mode are set to "Motion"). Liquid pipeline 346 supplies the hydraulic fluid from the solenoid S to the actuator 330C switch.

The solenoid 332D is in communication with the liquid pipe 152 and therefore supplied hydraulic fluid pressure delivered by the pump 118. The solenoid 332D passes hydraulic fluid to the actuator 330D switching fluid is STN pipe 348.

The solenoid E is in communication with the liquid pipe 152 and therefore supplied hydraulic fluid pressure delivered by the pump 118. The solenoid E transmits hydraulic fluid in the region EA switching liquid pipeline 350.

The solenoid 332F is in communication with the liquid pipe 152 and therefore supplied hydraulic fluid pressure delivered by the pump 118. The solenoid 332F transmits hydraulic fluid in the region 330Eb switching liquid pipeline 352.

On each of the actuators 330A-C switch is supplied lubrication oil in the liquid pipe 224. Each of the solenoids 332A-F and actuators 330D-E switch perform the release liquid pipeline 140. Relief valve 360 is in communication with liquid pipeline 140 is fixed to the preset pressure for regulating the pressure of hydraulic fluid in the liquid line 140. This ensures that the contours of the clutch remain full when they are not used to minimize the reaction time. In liquid tubing 140 is supplied to the oil pressure limiting supply. Each of the solenoids 332A-F is selected or as a normally closed or normally open, so you can access what is being the only transfer of default in case of loss of electrical power. For example, if you want the sixth gear ratio as the speed of the forward stroke by default during power loss, solenoids 332A-selectable normally open and the solenoids 332D-F selects normally closed.

In addition, each of the liquid line 336, 342, 346, 348, 350 and 352, which nourish actuators 330A-F switch, includes hole 354, located parallel one-way valve 356. Orientation is a one-way valve 356 such that the one-way valve 356 allows the message actuators 330A-E coupling with solenoids 332A-F and prevents fluid communication from the solenoids 332A-F actuators 330A-E switch. This device controls the oil flow to the actuators 330A-E switch through holes 354.

Description of the invention is merely exemplary in nature, and it is assumed that the variants that do not depart from the essence of the invention, are within the scope of this invention. Such options should not be regarded as a departure from the essence and scope of this invention.

1. System, subsystem containing the supply of hydraulic fluid to provide hydraulic fluid, having at least first and second pressure levels; the solenoid is lower in liquid flow communication with the engine supply of hydraulic fluid, the solenoid has a first operating mode and a second operating mode; valve site at the bottom for liquid flow communication with the engine supply of hydraulic fluid and a solenoid valve and the site has a cylindrical slide valve is moved between the first position and the second position, the valve Assembly provides the hydraulic fluid from the third pressure level, when the spool valve is in the first position; and a torque Converter having a fluid coupling mode and the direct drive and with the inlet of the torque Converter at the bottom for liquid flow communication with the valve site, the release of the torque Converter at the top for liquid flow communication with the valve site, the lockup clutch the torque Converter and actuating the clutch mechanism at the bottom for liquid flow communication with a solenoid made with the possibility of engagement of the clutch of torque Converter lock, when the cylindrical valve is in the first position and the solenoid is in the first operating mode, the torque Converter takes hydraulic fluid from the third pressure level to activate the fluid coupling, and when the cylindrical valve is in the second position and the solenoid is in the second operating mode, the torque Converter adopts hydraulic is idcast with the first pressure level to training mode liquid coupling, and actuating the clutch mechanism receives hydraulic fluid from the first pressure level to enable direct drive.

2. The system according to claim 1, additionally containing a radiator at the bottom for liquid flow communication with the release of the torque Converter through the valve site, when the cylindrical valve is in the first position, and at the bottom in liquid flow communication with the engine supply of hydraulic fluid through the valve site, when the cylindrical valve is in the second position.

3. The system according to claim 1, in which the solenoid moves the cylindrical spool from the first position to the second position when the solenoid is in the second operating position.

4. The system according to claim 1, additionally containing a drain valve at the bottom for liquid flow communication with the release of the torque Converter through the valve site, when the cylindrical valve is in the second position, and a drain valve that has the specified relief pressure, which maintains the pressure of hydraulic fluid in the torque Converter at or below a predetermined relief pressure.

5. The system according to claim 1, in which the hydraulic fluid from the third pressure level consists of combining valve site hydraulic fluid from the first pressure level and hydraulic fluid from the second uravneniya.

6. The system according to claim 5, in which the hydraulic fluid from the second pressure level is created from the valve block flow limitation and valve block pressure regulator at the bottom for liquid flow communication with the pump, and the hydraulic fluid from the first pressure level is created from the valve block flow limitation at the bottom for liquid flow communication with the pump.

7. The system according to claim 6, in which the hydraulic fluid from the third pressure level is communicated with a radiator, when the cylindrical valve is in the first position.

8. The system according to claim 5, additionally containing the first strip in fluid communication with hydraulic fluid from the first pressure level downstream from the valve block and the second gasket in fluid communication with hydraulic fluid from the second pressure level downstream from the valve block, and the first gasket has a bore diameter that is less than the diameter of the hole of the second strip.

9. The system according to claim 1, in which the actuator clutch is engaged with the torque Converter lockup clutch when the hydraulic fluid from the first pressure level is transmitted from the solenoid for actuating the clutch mechanism.

10. The system according to claim 1, in which the solenoid is a solenoid is a variable force and high consumption, which is all closed.



 

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The invention relates to a control system variable speed drive designed, for example, for use in the infinitely-variable transmission

FIELD: transport.

SUBSTANCE: proposed system comprises first source of pressurised hydraulic fluid source to produce first fluid flow and second source of pressurised hydraulic fluid source to produce second fluid flow, and torque converter control subsystem to control said converter and its coupling. Said subsystem comprises torque converter control valve and solenoid. Said solenoid is multiplexed to aforesaid control vale and coupling. Said control valve controls hydraulic fluid flow to torque converter and other subsystems in hydraulic control system.

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