JPH07269672A - Electro-hydraulic type adjusting gearing controller - Google Patents

Abstract

PURPOSE: To use the same basic unit by a master-slave principle and a partner principle by constituting a pressure regulating valve as a proportional valve, in a form in which one of primary and secondary pressure valves is constituted as a proportional valve and acts as a transmission pressure regulating valve, and the other acts as a pressure regulating valve. CONSTITUTION: In an electrohydraulic regulating and transmitting device control device for an electronically and continuously variable transmission device 10 of an automobile, a pump 23, a primary pressure valve 25 and a secondary pressure valve 30 are provided. The primary pressure valve 25 to be one of these pressure valves 25, 30 is constituted as a proportional valve to be two-edge controlled and acts as a transmission regulating valve and further the other secondary pressure valve 30 acts as a pressure regulating valve for regulating pressing force. In this type of regulating and transmitting device control device, the secondary pressure valve 30 acting as the pressure regulating valve is constituted to be a proportional valve to be two-edge controlled in the same way.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electrohydraulic regulating transmission control device for an electronically controlled continuously variable motor vehicle transmission of the type defined in claim 1.

[0002]

2. Description of the Related Art An electro-hydraulic regulating transmission control device of the type mentioned above is, for example, HR per: Status der CVT-Entwicklung-Vo.
rteile und Grenzen des Systems, 2.Aachener Kolloqui
Um, Fahrzeug-und Motortechnik '89. (CVT = Continuously Variable Transmission) is performed by one of two known principles, a partner principle or a master-slave principle.

According to the master-slave principle, the pistons in the disk pair on the input side and the output side have a surface ratio of approximately 2: 1. In this case, the pistons of the primary and secondary disc pairs are usually controlled by two separate valves, a primary pressure valve and a secondary pressure valve. The primary pressure valve, which is assigned to the primary side or the input side, is usually configured as a two-edge controlled proportional valve and regulates the transmission ratio of the transmission. The secondary pressure valve is usually constructed as a proportional pressure regulating valve with single edge control and regulates the belt tension via the reactive pressure.

In the case of the partner principle, the disk pairs on the input side and the output side usually have the same surface ratio. In this case both pistons are controlled by a proportional valve with four-edge control. This proportional valve serves both to adjust the transmission ratio and to maintain the required pressure ratio on both piston faces. In this case, a proportional pressure regulating valve on the outlet side serves to regulate the basic pressure level. A pressure limiting valve is additionally arranged on the pressure side, which is additionally associated with the pump. Electrohydraulic regulating transmissions for the partner principle and the master-slave principle A control device usually has a complete structure with other basic structures and other valve functions when switching from one control variation to another. Different hydraulic control devices are configured as required with correspondingly different requirements for electrical control signals.

[0005]

The object of the present invention is to make it possible to use the same basic unit of an electrohydraulic control device in both control schemes, namely in the master-slave principle and in the partner principle.

[0006]

The object of the invention is solved by an adjusting transmission control device having the features of claim 1.

[0007]

The same adjusting magnet can be used for controlling both regulating valves of the basic unit. The use of two proportional valves with two-edge control results in a basic unit of electrohydraulic regulating transmission control device whose control principle can be changed by using easily replaceable extraction components. Changes in the hydraulic connection of the individual components can be realized, for example, by means of suitable passage configurations and the use of assembly members or intermediate members in the basic unit. This provides a cost advantage when constructing a hydraulic controller, since the basic unit can be used for both control principles. Furthermore, the functions already known by the master-slave principle,
For example, stepless transmission ratio adjustment when the electrical control signal is lost can be diverted to the partner principle. It is particularly advantageous that the basic unit has both a proportional pressure valve and a pressure regulating valve for limiting the maximum pressure, the outlet volume flow of this pressure regulating valve being connected to a consumer connected downstream, for example a clutch or It is to be supplied to the lubricating device. The pressure limiting valve prevents a predetermined maximum pressure from being exceeded at the limit of the pressure regulation range.

A further advantage is that the basic unit is provided with an additional pressure limiting valve, the reactive pressure of this additional pressure limiting valve being higher than the reactive pressure of the pressure limiting valve, which is connected to the pressure medium tank. is there. This additional pressure limiting valve avoids the potentially high pressure rises that can occur if the consumer connected behind the pressure limiting valve fails or if the pressure medium is not removed. To increase the safety of the electro-hydraulic regulating transmission control device even in the event of an electronic control failure, a measuring throttle or throttling point connected to a switching valve is located at the branch of the outlet conduit leading to the subsequent consumer. And is adapted to control the transfer ratio adjusting valve when the switching valve exceeds a predetermined pressure. This ensures a reliable transmission ratio adjustment regardless of the pressure ratio in the primary disk pair or secondary disk pair,
It is also ensured in case of electrical control failure. The measuring throttle and the switching valve are advantageously integrated in the basic unit.

A further advantage is that the primary pressure valve is followed by a throttle section with a fixed or variable cross section, which throttle station prevents a rapid outflow of pressure medium in failsafe operation. . In order to avoid the effects of pressure peaks, it is expedient to place a damping device, for example a throttle, on at least one of the pressure conduits which load the disc pair.

In order to switch the basic unit of an electrohydraulic regulating transmission control device, for example from the master-slave principle to the partner principle, a system pressure valve is assigned to this basic unit, which on one side is pumped by the pump pressure. On the one hand, and on the other hand with one crimping pressure and spring force of both disc pairs.

The basic unit of the electrohydraulic regulating transmission control device remains largely unchanged. That is, the basic unit is 1
Only the valve function of the next pressure valve is different. By changing the valve slider without changing the valve casing of the primary pressure valve, said change is possible in a simple manner. The valve structures of the other valve groups of the basic unit and the adjusting magnets of both proportional magnets are maintained.

By placing an alternating valve between both pressure chambers of the disc pair and the supply conduit on the spring side of the system pressure valve,
It is always guaranteed in a simple manner that the system pressure valve is supplied with both higher pressures.

By arranging the switching valve between the primary pressure valve and the secondary pressure valve, during failsafe operation of the regulating transmission control device, the valve with the lower pressure level always takes over the transmission ratio regulation. Guaranteed.

Advantageous further developments and further advantages of the invention are described in the subclaims 2 and the following text.

[0015]

1 and 2, a continuously variable transmission (winding transmission, known per se at 10) is known.
Continuously Variable Variable Tra
nsmission) is shown. Transmission means is fastened between the primary disk pair 11 and the secondary disk pair 12 of this transmission. This transmission means can be, for example, a belt, a push ring belt or a chain. The primary disk pair 11 and the secondary disk pair 12 are one fixed disk 14 or 15 and the movable disk 1 which is movable in the axial direction.
6 or 17. A pressure chamber 18 is arranged in the movable disc 16 of the primary disc pair. This pressure chamber 18
Are loaded via the primary pressure conduit 19. Secondary disk pair 1
A secondary pressure chamber 20 is similarly arranged in the second movable disk 17. This secondary pressure chamber 20 is loaded via a secondary pressure conduit 21. The primary and secondary disc pairs 11 or 12 cooperate in the illustrated embodiment on a master-slave principle. That is, the ratio of effective pressure surfaces of the movable disks 16 or 17 of both the primary disk pair 11 or the secondary disk pair 12 is, for example, 2: 1. Both pressure chambers are pressure-loaded by the hydraulic pump 23. The hydraulic pump 23 can be, for example, a gear pump driven by an internal combustion engine of an automobile. The hydraulic pump 23 sucks the pressure medium from the tank 27 and is connected to the primary pressure valve 25 via the pressure conduit 24. A primary pressure line 19 extends from the primary pressure valve 25 on the one hand and a return line 26 to the tank 27 on the other hand. A throttling point 29 is arranged in the return conduit 26. This throttling point 29 can have a fixed or variable cross section. A branch 28 leads from the pressure conduit 24 to a secondary pressure valve 30. This secondary pressure valve 30 is connected on the one hand to the secondary pressure conduit 21 and on the other hand to the outflow conduit 31. This outflow conduit 31 leads to the next consumer, for example a clutch or a lubrication device.

The primary pressure valve 25 is constructed as a 3/2 proportional valve, and the valve slider 32 of this 3/2 proportional valve is moved in the valve casing valve hole by a proportional adjusting magnet 34 against the action of a compression spring 35. It is possible. In this case, the valve slider 32
And the valve hole 33 is set so that the primary pressure valve takes the neutral position I on the left side when no current is passed through the proportional adjustment magnet 34 and takes the switching position II when the proportional adjustment magnet 34 is fully fed with current. It is configured. The transition between these two switching positions is continuous or fluid. In this case the valves can be constructed with zero overlap or with negative overlap or positive overlap. In the switching position I or the corresponding end position, the pressure line 24 is closed on one side, whereas the primary pressure line 19 and the return line 26 are connected to one another. In the switching position II, the pressure line 24 and the primary pressure line 19 are connected to one another, whereas the return line 26 is closed on one side. A control conduit is open on each end of the valve slider 32. Of these control conduits, the left control conduit 36 is connected to the tank 27. Control conduit 37 on the right is pin 3
9 loads the protruding ring surface 38 and is connected to a switching valve 40 which will be described in detail below. To this end, the valve hole 33 is provided with four control ring grooves, which are designated consecutively 41 to 44 from left to right. The first control ring groove 41 is connected to the pressure conduit 24, the second control ring groove 42 is connected to the primary pressure conduit 19, the third control ring groove 43 is connected to the return conduit 26, and the fourth control ring groove 43 is connected to the return conduit 26. The control ring groove 44 is connected to the right control conduit 37. Two
The ring grooves 45 and 46 arranged on the right of the two tanks 27
It is connected to the valve or serves to lead the oil leakage of the proportional magnet. The valve slider 32 also has two slider sections that slide liquid-tight in the valve bore, namely a left slider section 47 and a right slider section 48, with a smaller diameter between these slider sections 47 and 48. A web 49 is arranged. In the embodiment of the primary pressure valve shown in FIG. 2 and in the switching position shown, the primary pressure valve is in a zero overlap condition. That is, the left slider section 47 closes the first control ring groove 41, while the right slider section 48 closes the control ring groove 43. The compression spring 35 acts on the left end surface of the valve slider 32, while the protruding rod of the proportional adjustment magnet 34 contacts the right end surface.

The secondary pressure valve 30 is likewise designed as a 3/2 proportional valve and the valve hole 51 likewise comprises four control ring grooves. These control ring grooves are designated 52-55 consecutively from the left. The first control ring groove 52 is connected to the outflow conduit 31, the second control ring groove 53 is connected to the secondary pressure conduit 21, the third control ring groove 54 is connected to the branch portion 28, and the fourth control ring groove 54 is connected to the branch portion 28. The control ring groove 55 is connected to the tank 27 via a control conduit 56. The additional ring groove 57 is likewise connected to the tank 27 and serves to guide the leakage oil from the valve and the proportional control magnet 58. The protruding rod of the proportional adjustment magnet 58 is in contact with the right end surface of the valve slider 60, which has the compression spring 61 supported on the left end surface side. The pressure chamber at the end surface of the left slider is released to the tank 27 via the control conduit 62. In the valve slider 60, the secondary pressure valve 30 is in the left neutral position I with no current flowing through the proportional adjustment magnet, and in this neutral position I, the outflow conduit 31 is closed on one side and the branch portion 2
8 and the secondary pressure conduit 21 are connected to each other. When current is applied to the proportional adjustment magnet, the secondary pressure valve is adjusted to the switching position II against the action of the compression spring 61. In this switching position II, the branch 28 is connected to the primary pressure conduit 21 and the outflow conduit 31. The transition between the neutral position I and the switching position II is again continuous. For this purpose, the valve slider 60
Are connected together by a small diameter web 65
It has one slider section, a left slider section 63 and a right slider section 64. In the embodiment shown in FIG. 2 and the switching position of the secondary pressure valve, the secondary pressure valve is in the neutral position I. That is, the left slider section 63 closes the first control ring groove 52 and thus the outflow conduit 32, while the right slider section 64 is located between the third and fourth control ring grooves. By applying an electric current to the proportional adjustment magnet 58, the valve slider 60 is moved to the compression spring 61.
Is moved to the left against the action of the control valve, the right control edge of the left slider section 63 opens the ring groove 52 and thus the connection between the control ring grooves 52, 53, 54.
The right slider section 64 is located between the third and fourth control ring grooves 54 or 65 in any switching position of the valve slider 60 without changing the control cross section of the third control ring groove 54. .

The primary pressure valve 25 works as a transmission adjusting valve according to the master-slave principle, and the secondary pressure valve 30 works as a pressure adjusting valve.

An inlet conduit 70 of the pressure limiting valve 71 branches from the pressure conduit 24 between the primary pressure valve 25 and the hydraulic pump 23. The outlet conduit 72 of this pressure limiting valve 71 is connected to the outflow conduit 31 via a throttling point 73. The pressure limiting valve is loaded on the one hand by the compression spring 74 and on the other hand by the pressure in the control line 75. This control conduit is connected to the inlet conduit 70.

Further, from the pressure conduit 24, an inlet conduit 77 of the additional pressure limiting valve 78 branches, and its outlet conduit 79.
Is connected to the tank 27. The additional pressure limiting valve 78 is likewise loaded on one side by a compression spring 80 and on the other side by the pressure of a control conduit 81 connected with an inlet conduit 77. The additional pressure limiting valve 78 is the pressure limiting valve 7.
It responds only when it receives a pressure higher than the response pressure of 1.
A control conduit 83 extends from the outlet conduit 72 of the pressure limiting valve 71 towards the switching valve 40. This switching valve 40 is connected on the one hand to the control conduit 37 to the right of the primary pressure valve,
On the other hand, it is connected to the tank 27 via a return conduit 84. The switching valve 40 is configured as a 3/2 switching valve,
It is loaded on one side with a compression spring 85 and on the other side with the pressure of a control conduit 86 connected to the pressure conduit 24. When the force due to the action of the compression spring 85 is greater than the opposite force action due to the pressure in the control conduit 86, the switching valve 40 controls the right side of the primary pressure valve 25 with the control conduit 83 closed on one side. The conduit 37 and the return conduit 84 are located in a switching position I where they are connected to each other. When the force due to the pressure effect in the control conduit 86 exceeds the effect of the force of the compression spring 85, the switching valve 40 is adjusted to the right switching position II and the control conduit 83 to the control conduit 37 to the right of the primary pressure valve.
Connected with. In this case, the return conduit 84 is closed on one side.

The pressure limiting valve 71, the additional pressure limiting valve 78 and the switching valve 40 can be constructed in the valve unit 90 in a simple manner. One example of such a valve unit 90 is shown in FIG.
Is shown in.

The valve unit 90 integrates the functions of the valves 71, 78, 40 into a single valve member with a valve slider 91 having three slider sections 92 to 94. The right slider section 92 and the central slider section 93 are joined together by a small diameter web 95, while the central slider section 93 and the right slider section 94 are joined together by a small diameter web 96. . The valve slider 91 is guided in a valve hole 98 in a liquid-tight manner, which valve hole 98 is provided with six control ring grooves, which are shown consecutively from left to right by the reference numerals 99 to 104. The first control ring groove 99 is connected to the pressure conduit 24. The second control ring groove 100 and the fourth control ring groove 102 are connected to the control conduit 37 on the right side of the primary pressure valve 25. Third control ring groove 101
And the sixth control ring groove 104 are connected to the tank 27, respectively. The fifth control ring groove 103 is the drawing point 7
It is connected via 3 to the outflow conduit 31. The valve slider 91 has a slider section 92 on the left side of the first control ring groove 9
9 is configured to cooperate. The central slider section 93 is located in the area of the second control ring groove 100 and extends into the intermediate chamber between the third control ring groove 101 and the fourth control ring groove 102. Right slider section 9
4 cooperates with the fifth and sixth control ring grooves 103 and 104. The control slider 91 is loaded with the pressure in the pressure conduit 24 at its left end face. For this purpose a suitable pressure chamber 105 is connected to the pressure conduit 24. The right end surface of the valve slider 91 is loaded by the compression spring 106, and the pressure chamber on the right end surface is released to the tank 27.
The compression spring 106 replaces the three single valve member compression springs 74, 85, 80 in this embodiment. Valve slider 9
1 is moved to the right against the action of the compression spring 106 under the action of the pressure in the pressure conduit 24 or the pressure chamber 105. When the pressure in the pressure conduit 24 or the pressure chamber 105 exceeds a predetermined value, the valve slider 91 is moved to the right against the action of the compression spring 106. In this case, the pressure medium reaches the outflow conduit 31 having a low pressure level from the ring groove 73 adjacent to the ring groove 101 and the ring groove 102 via the throttle portion 73. This valve function corresponds to that of the pressure limiting valve 71. Another safety feature is to provide the primary pressure valve 25 with a pump displacement and thus a pressure related to the motor speed in order to guarantee a transfer regulation related to the pump displacement in case of electronic control failure. is there. When the valve slider 91 is in the left starting position, the right control conduit 37 is connected to the tank 27 via the control ring groove 102 and the control ring groove 101. In this case, the control ring groove 1
00 and the control ring groove 103 are covered by a central or right slider section 93 or 94. An adjusting pressure corresponding to the tank pressure acts on the right end surface of the valve slider 32 of the primary valve 25. Pressure chamber 105 or pressure conduit 2
When the system pressure in 4 rises above the critical value, the switching process first disconnects the ring grooves 101 and 102 and connects the ring grooves 102 and 103 to each other. This allows the control conduit 37 on the right side of the primary pressure valve to
Then, the pressure generated at the throttle point 73 is formed. As the system pressure continues to rise, the valve slider 91 is moved further to the right, thus making the connection between the ring groove 99 and the ring groove 100. The pressure medium not required for the transmission adjustment can escape via the connection between the ring groove 100 and the ring groove 102 as well as the connection to the ring groove 13 via the throttling point 73 to the outflow conduit. At the throttle point 73, a pressure drop occurs according to the oil discharge amount. This pressure drop makes a transmission adjustment in the primary valve via the control conduit 37 on the right side. When the pressure is further increased, the control grooves 102 and 104 are connected to each other,
The excess oil volume flow can be directed directly to the tank 27. This valve function corresponds to the valve function of the additional pressure limiting valve 80.

In order to avoid the occurrence of pressure peaks or pressure fluctuations, for example, a buffer throttle 109 is provided in the primary pressure conduit 19.
Are arranged.

3 and 4 show a regulating transmission control device which works on the partner principle. In this case, the same components are designated by the same reference numerals, and functionally the same components are designated by the same reference numerals with the addition of a capital letter. The transmission 10A differs from the above-mentioned transmission by the change in the dimensional ratio of the movable disk of the primary disk pair 11A and the secondary disk pair 12A. The effective pressure surface area ratio is 1: 1 but it is possible to have ratios other than 1 if the controls are properly adapted. The control of the primary disk pair 11A is performed by the primary pressure valve 25 as in the previous embodiment.
The oil is supplied to the next disk pair 12A through the secondary pressure valve 30A. The secondary pressure valve 30A is connected to the branch 28, the outflow conduit 31 and the secondary pressure conduit 21 as in the previous example of use. However, the function of the secondary pressure valve 30A is different from the valve function of the above secondary pressure valve 30. In the neutral position I, the branch 28 is closed on one side, whereas the primary pressure conduit 21 and the outflow conduit 31 are connected to each other. In the switching position II, the outflow conduit 31 is closed on one side, whereas the branch 28 and the secondary pressure conduit 21 are connected to each other. This change in valve function is made by replacing the valve slider. That is, by using a modified valve slider 60A. However 2
The casing structure of the secondary pressure valve remains unchanged. That is, valve hole 3
3 and 4 control ring grooves 52 to 55 and ring groove 5
7 does not change. Further, the proportional adjustment magnet 58 is also the same. However, unlike the secondary pressure valve 30, the conduit circuit is changed in the secondary pressure valve 30A. The first control ring groove 52 is connected to the return conduit 31. The second control ring groove 53 is connected to the secondary pressure conduit 21,
The third control ring groove 54 is connected to the branch portion 28, and
The control ring groove 55 is connected to the control conduit 56A. The ring groove 57 is connected to the tank 27 as described above. The valve slider 60A is loaded by the compression spring 61 on the left end face, and the pressure chamber on the left end face is released to the tank 27 as in the previous embodiment. The valve slider 60A also has two slider sections 63A and 63B.
And a web 65A between them. In this case, the left slider section 63A has the first control ring groove 5
2, while the right slider section 64 has a third
Of the control ring section 54. The secondary pressure valve 30A can be configured with zero overlap or positive or negative overlap. In this embodiment and the switching position shown in FIG. 4, the valve slider 60A is in the region of zero overlap. That is, the first control ring groove 52 and the third control ring groove 54 are respectively covered by the left or right slider section. At the neutral position I of the secondary pressure valve 30A, since the valve slider is moved to the right under the action of the compression spring 61, the second and third ring grooves 53 and 54 are connected to each other. , The first control groove 52 remains covered. When the valve slider is moved to the switching position II against the action of the compression spring 61 by applying a current to the proportional adjustment magnet 58, the third control ring groove 54 is covered by the right slider section 64A. In contrast,
Both control grooves 52, 53 are connected to each other. The fourth ring groove 55 is connected to the ring groove 45 of the primary pressure valve 25 via the control conduit 56A. The pressure generated thereby loads the end face of the pin 39.

In addition to the primary pressure valve 25 and the secondary pressure valve 30A, the system pressure valve 110 is required for the operation of the adjusting transmission control device based on the partner principle. This system pressure valve 110 is connected via its inlet conduit 111 to the branch 28 and via its outlet conduit 112 to an outlet conduit 31.
Connected with. The valve slider 113 is loaded by the inlet pressure on the left end face via the left control conduit 114. That is, it is loaded by the pressure in the inlet conduit 111 or the branch 28. The opposite end face is a compression spring 11
It is loaded by a force of 5 and a pressure in the right control conduit 116. The right control conduit 116 is connected to the alternating valve 120. On the one hand, this alternating valve 120
It is connected via 1 to the primary pressure conduit 19 and, on the other hand, via the secondary branch 122 to the secondary pressure conduit 21. Through this alternating valve 120, the right end surface of the valve slider 113 or the control conduit 116 on the right side is always loaded with the higher pressure of both pressures in the primary or secondary conduit. The valve slider 113 of the system pressure valve 110 causes the inlet conduit 111 and the outlet to exit when the pressure-based force effect in the left control conduit 114 is greater than the sum of the direct effects of the compression spring 115 and the right control conduit 116 pressure. A pressure medium connection with the conduit 112 is configured to be formed. With this system pressure valve 110, the system pressure in the pressure conduit 24 or the branch 28 is always the value Δ.
Only p is kept above the higher of both pressures in the primary pressure conduit 19 or the secondary pressure conduit 21. in this case,
A pressure rise of Δp is generated on the effective piston surface of the valve slider 113 based on the ratio of the pressure and the force of the compression spring 115. In this case, the effective pressure surface on the piston surface or on the valve slider can be of different sizes.

A switching valve 125 is arranged between the switching valve 40 of the valve unit 90 and the control conduit 56A between the primary and secondary pressure valves 25 or 30A. This is 3/2
The switching valve 125, on the one hand, the right control conduit 37
Is connected between the switching valve 40 and the primary pressure valve 25. Another connection is the control branch 126 which is connected between the control conduit 56A and the primary pressure valve 25 and the secondary pressure valve 30A.
Made through. The third connecting portion 127 is connected to the tank 27. The switching valve 125 has a switching position I on the left side.
At one end the connection 127 to the tank 27 is closed and on the other hand the control conduit 37 or 37A and the connection 12
A connection is made with 6. In the switching position II on the right side, the connection 37A to the control conduit 37 is closed on one side,
The control branch 126 is connected to the connection 127, and thus to the tank 27.
Connected with. The control slider 128 is connected at its left end face to the primary branch 121 via a control conduit 129, and at the right end face is connected to a secondary branch 122 via a second control conduit 130. The right end face of the control slider 128 is additionally loaded by the force of the compression spring 131. In the fail-safe operation of the electrohydraulic regulating transmission control device based on the partner principle, if the electrical control of the primary and secondary pressure valves fails, only the pressure valve with the lower pressure level will be the transmission regulation. Suitable for. In the operation of the regulating transmission control device, the pressure curve shown in FIG. The pressure PPrim in the primary pressure conduit remains approximately constant, while the pressure Psec in the secondary pressure conduit falls in a straight line. The system pressure P pump is always a value Δp due to the system pressure valve 110 and the alternating valve 120.
Only kept on the higher side of both pressures. In the range of the transmission ratio indicated by the symbol iA, pressure equilibrium occurs between the primary pressure and the secondary pressure. In the range between the maximum transmission transmission ratio and iA, the primary pressure valve is involved in the transmission adjustment in fail-safe operation, whereas in the range between iA and imin the secondary pressure in fail-safe operation. Alternatively, the secondary pressure valve is involved in adjusting the transmission ratio. If, for example, the control electronics of the regulating transmission control device fails during traveling at high travel speeds and the transmission transmission ratio is in the range between iA and imin, the changeover valve 125 is additionally mounted on the right slider surface. It is switched to the switching position II on the basis of the acting force of the compression spring 130. In this case, the transmission adjustment is performed by the secondary pressure valve 30A. The pressure in the control conduit 56A then acts on the right ring end face of the valve slider 60A of the secondary pressure valve. If an excessively high adjusting pressure is generated in front of the throttle portion 73 due to the motor rotation speed being too high, and thus the pump discharge rate being too high, the valve slider 60A is pushed to the left against the action of the compression spring 61. Be done. This causes the pressure medium to flow from the secondary pressure conduit 21 to the ring groove 53.
It is possible to escape to the outflow conduit 31 via 52 and 52.
This reduces the transmission ratio and thus the motor speed. On the other hand, if the regulation pressure is too low, the pressure medium reaches the secondary pressure conduit 21 from the branch 28 or the pressure conduit 24 via the ring grooves 54 and 53.

In the valve slider 32 of the primary pressure valve 25, the pressure in the control conduit 56A or the control conduit 37 acts on the right ring end surface and the right ring end surface and the right end surface, so that the valve slider acts as a compression spring. Against the stopper against the left side. This causes the pressure medium to flow from the pressure conduit 24 through the ring grooves 41, 42
It is supplied to the next pressure conduit 19.

When the switching point or the switching transmission ratio iA is reached or exceeded, the valve slider 128 of the switching valve 125 is moved to the left. In this case, the transmission adjustment is performed by the primary pressure valve 25. That is, the transfer ratio is i
It can vary between max and iA. In this case, the switching point or the switching transmission ratio must be selected so as to prevent over rotation of the motor. The adjusted pressure in the right control conduit 37 is effective for adjusting the transmission ratio using the primary pressure valve. This adjusting pressure is guided to the ring end surface 38 of the valve slider via the control ring groove 44. If the regulating pressure is too high, the pressure medium reaches the primary pressure conduit 19 from the pressure conduit 24, whereas if the regulating pressure is too low, the pressure medium flows from the primary pressure conduit via the ring groove 43 into the tank 27. You can escape to. Since the secondary pressure valve 30A is at the right end position in this transmission ratio adjusting process, the system pressure from the pressure conduit 24 or the branch 28 is generated in the secondary pressure conduit 21. In this case, by means of the throttle 29, particularly in the case of a malfunction of the control electronics, that is to say when the valve slider 32 of the primary pressure valve 25 is initially in the right-hand end position, a particularly rapid transmission ratio adjustment is directed towards the maximum transmission ratio. Guarantee that it is not possible. In this case, the pressure medium does not reach the conduit 31 from the conduit 24 via the pressure limiting valve 71 and the throttling point 73, since the total pump displacement is effective for adjusting the transmission ratio. In this case, the switching valve 40
At, no regulating pressure is created. The diaphragm 29 may have a fixed or variable diameter for this purpose.

The basic unit of the electro-hydraulic type adjustment transmission control device is a primary pressure valve 25 and a secondary pressure valve 30 or 3.
It has 0A. In addition to this, a valve unit 90 or valves 71, 40 and 78 can be provided in this basic unit. This basic unit can be integrated in the valve block in a simple manner. By exchanging the valve sliders in the secondary pressure valve 30 or 30A and connecting the system pressure valve 110 and optionally the alternating valve 120, the regulating transmission control device is in a simple and advantageous manner from master-slave principle to partner principle. Can be transferred. By additionally connecting the switching valve 125, it is possible to improve the operational reliability of the adjustment transmission control device according to the partner principle. These additional valves can also be incorporated in a separate valve block which is connected to the standard valve block of the basic unit, for example via an intermediate plate. The adaptation in the conduit circuit required here is achieved either by a modified hole pattern in the intermediate plate or by laying the passage guides in separate valve blocks. Forming the basic unit or standard valve block provides significant cost advantages in fabrication. This is because the field of use in which such a basic unit of the adjusting transmission control device can be used is further expanded.

FIG. 6 shows a pressure limiting valve 71 and an additional pressure limiting valve 8.
A variant embodiment of a valve unit 90 is shown in which the functions of 0 and the switching valve 80 are arranged in two valve members. In this case, the first pressure valve 135 serves to limit the pressure, whereas the additional valve 136 transmits from the predetermined limit pressure to the switching valve 125 the pressure before the throttling point 73, which is important for the transmission regulation. . In this case, the valve slider 137 of the pressure valve 135
Is loaded on one side with the pressure in the pressure conduit 24 via the control conduit 138, while on the other side the compression spring 13
9 is working. In relation to the pressure in the pressure conduit 24, the valve slider 137 is moved against the action of the compression spring. Once the predetermined pressure is exceeded, the connection between the pressure conduit 24 and the outlet conduit 72 is made. If this pressure is exceeded further, the valve slider 137 is moved further to the right, so that the pressure medium connection 79A to the tank 27 is then opened.

The valve slider 141 of the additional valve 136 is loaded on one end face side by the pressure in the pressure conduit 24 via the control conduit 142, while on the other end face side the force of the compression spring 143 acts. There is. When the predetermined pressure is exceeded, the connection between the control line 37A and the tank 27 is interrupted and at the same time the connection between the control line 37A and the throttling point 73 is made.

A possible embodiment of the alternating valve 120 is shown in FIGS. 7a to 7d. Hollow cylindrical valve bodies 145a to 145d in all four embodiments of the alternating valve.
Up to the same, these hollow cylindrical valve bodies are divided into two sections by an inner separating wall 146 extending approximately centrally in the first, third and fourth embodiments. In the second embodiment, this separation takes place in the press-fitted balls 147. In each of the four embodiments, the valve bodies 145a to 145d are loaded with the pressure in the primary branch portion 121 on one end face and the pressure in the secondary branch portion 122 on the opposite end face. Furthermore, each valve body cooperates with a control ring groove 148 extending around its circumference and connected to the right control conduit 116. On the upper side and the lower side of the separating wall 146 or the separating sphere 147, different throttle openings 150 penetrating the walls of the valve bodies 145a to 145d are provided. Each of these diaphragm openings 150 cooperates with a control groove 148. In this case, the aperture opening can be arranged such that it has a positive or negative or zero overlap in relation to the ring groove 148, depending on the use or configuration of the adjusting transmission control device.
In addition to the pressure load on both end faces of the valve body, the valve body 145a is loaded on both sides by the force of the spring 151 or 152.

FIG. 8 shows, for example, a valve 155 for reverse gear safety means.
7 illustrates a modified embodiment of the diaphragm 29 as may be integrated therein. In this case, the control ring groove 4 of the primary pressure valve 25
3 is connected on the one hand to the tank 27 via a fixed throttle 156 and on the other hand to the ring chamber 157 between the slider sections 158, 159 of the valve slider 160 of the valve 155. In the forward traveling operation of the adjustment transmission control device, the adjusting magnet 161 of the valve 155 is controlled via the control device (not shown), and the valve slider 160 is compressed by the compression spring 162.
It is pressed against the stopper against the action of. In this switching position, a connection is made between the ring groove 43 of the primary pressure valve 25 and the tank 27 via the ring chamber 157, so that the pressure medium can flow out unhindered.
If the control of the adjusting magnet 161 also fails due to a failure of the electronic control, the valve slider 160 is moved to the neutral position by the action of the compression spring 162. In this switching position of the valve slider 160, the slider section 158 cuts off the connection of the ring chamber 157 to the tank 27, so that the pressure medium passes from the ring chamber 157 of the primary pressure valve only through the throttle 156 and thus the small throttle crossing. Tank 27 through the surface
You will be able to escape to. Opening and closing of the flow cross section, as shown for example in valve 155, can be done with any valve member principle controlled directly by magnets.

[Brief description of drawings]

FIG. 1 is a principle circuit diagram of an adjusting transmission control device for the master-slave principle.

FIG. 2 is a simplified diagram of the constituent members of this principle circuit diagram.

FIG. 3 shows the principle circuit diagram of the adjusting transmission control device for the partner principle.

FIG. 4 is a simplified diagram of the components of FIG.

FIG. 5 is a diagram showing the progression of the primary pressure and the secondary pressure related to the transmission ratio according to the partner principle.

FIG. 6 is a diagram showing a modified embodiment of a valve group.

FIG. 7 is a view showing four embodiments of the alternating valve.

FIG. 8 is a diagram schematically showing the structure of an additional valve.

[Explanation of symbols]

10 transmission device, 11 primary disk pair, 12 secondary disk pair, 13 transmission member, 14 and 15 fixed disk,
16, 17 movable disk, 18 pressure chamber, 19 primary pressure conduit, 20 secondary pressure chamber, 21 secondary pressure conduit, 23 hydraulic pump, 24 pressure conduit, 25
Primary pressure valve, 26 return conduit, 27 tank, 28
Branch part, 29 throttling part, 30 secondary pressure valve,
31 outflow conduit, 32 valve slider, 33 valve hole,
34 proportional adjustment magnet, 35 compression spring, 36, 37
Control conduit, 38 ring surface, 39 pin, 40
Switching valve, 41, 42, 43, 44 control ring groove,
45,46 ring groove, 47,48 slider section, 51 valve hole, 52,53,54,55 control ring groove, 56 control conduit, 57 ring groove, 58
Proportional adjustment magnet, 60 valve slider, 61 compression spring,
62 control conduit, 63, 64 slider section, 7
0 inlet conduit, 71 pressure limiting valve, 72 outlet conduit, 73 throttling part, 74 compression spring, 75 control conduit, 77 inlet conduit, 78 additional pressure limiting valve,
79 outlet conduit, 80 compression spring, 81 control conduit, 83 control conduit, 84 return conduit, 85 compression spring, 86 control conduit, 90 valve unit, 9
1 valve slider, 92, 93, 94 slider section,
95 webs, 96 webs, 98 valve holes, 9
9 100, 101, 102, 103, 104 control ring groove, 105 pressure chamber, 106 compression spring, 1
10 system pressure valve, 111 inlet conduit, 112
Outlet conduit, 113 valve slider, 114 control conduit,
115 compression spring, 116 control conduit, 120
Alternating valve, 121 primary branch, 125 switching valve,
130 compression springs, 135 pressure valves, 136 additional valves, 137 valve sliders, 141 valve sliders,
142 control conduit, 143 compression spring, 145
a, 145b, 145c, 145d Valve body, 146
Separation wall, 147 balls, 148 control ring groove, 15
0 diaphragm opening, 156 diaphragm, 157 ring chamber,
158, 159 slider section, 160 valve slider, 161 adjusting magnet, 162 compression spring

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Peter Boyerle, Federal Republic of Germany Ludwigsburg Ballinger Strasse 24

Claims (10)

[Claims] 1. An electrohydraulic regulating transmission control device for an electronic continuously variable transmission (10) of a motor vehicle, comprising a pump (23) and a primary pressure valve (25). Two
A pressure regulating valve having a secondary pressure valve (30, 30A), one of these pressure valves being configured as a two-edge controlled proportional valve and acting as a transmission regulating valve and the other for regulating the crimping force. Of the type acting as, the electrohydraulic regulating transmission control device, characterized in that the pressure regulating valve is likewise configured as a proportional valve with two-edge control. 2. A pressure limiting valve (7) for limiting the maximum pressure.
2. The electrohydraulic regulating transmission control device according to claim 1, wherein 1) is provided and the outlet volume flow of this pressure limiting valve (71) is fed to a downstream connected consumer. 3. An additional pressure limiting valve (78) is provided in the conduit (24) for guiding the pump pressure, the responsive pressure of this additional pressure limiting valve (78) being greater than the responsive pressure of the pressure limiting valve (71). Adjusting transmission control device according to claim 2, characterized in that the additional pressure limiting valve (78) is connected to the pressure medium tank (27). 4. A throttle portion (73) is arranged at a branch portion (72, 83) of the outflow conduit (31) of the secondary pressure valve (30, 30A), and the throttle portion (73) is a switching valve (73). 40)
The pressure valve (25, 3) which is connected to the switching valve (40) and adjusts the transmission ratio when the switching valve (40) exceeds a predetermined pressure.
0, 30A) for controlling the electro-hydraulic adjusting transmission control device according to any one of claims 1 to 3. 5. Outflow conduit (26) of the primary pressure valve (25)
5. A diaphragm device (29) is arranged in the housing.
An electro-hydraulic adjustment transmission control device according to any one of items 1 to 7. 6. The throttle device (29) is variable, and the throttle device (29) is used in emergency operation of the adjusting transmission control device.
6. The adjusting transmission control device according to claim 5, wherein the cross section of the device is reduced. 7. A pair of discs (11, 11A, 12, 12A)
7. A shock absorber (109) is arranged in at least one of the pressure conduits (19, 21) for loading the load.
The adjustment transmission control device according to any one of items 1 to 7. 8. A system pressure valve (110) is arranged in the pump pressure conduit (24, 28), the system pressure valve being loaded on the one hand by the pressure in the pump pressure conduit and on the other hand by a pair of discs (11, 11A). , 12, 12A) and the adjusting transmission control device according to any one of claims 1 to 7, which is loaded by the pressure prevailing in the spring and the force of the spring (115). 9. An alternating valve (120) is arranged in the supply conduit (116) on the side of spring pressure to the system pressure valve (110), which valve always supplies the system pressure valve with the higher of both disc crimp pressures. The adjustment transmission control device according to claim 8. 10. A primary valve (25) and a secondary valve (30, 30)
10. A switching valve (130) is arranged between A), which switching valve always has a lower pressure level involved in the transmission ratio adjustment in the fail-safe operation of the control transmission. The adjustment transmission control device according to any one of claims 1 to 4.