JP2005106131A - Characteristic correction device for proportional solenoid control valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a characteristic correction device for a proportional solenoid control device that materialize accurate and simple inspection/correction from a viewpoint of quality stability of an automatic transmission. <P>SOLUTION: The characteristic correction device for the proportional solenoid control valve executes characteristic connection processing of the proportional solenoid control valve according to a behavior of a clutch piston. The characteristic correction device for the proportional solenoid control valve executes an inspection pattern wherein A(mA) is a zero value, B(mA) is a precharge pressure equivalent current value, C(mA) is the MAX current value equivalent to the maximum hydraulic pressure value, D(mA) is an upper side current value of an I-P correcting point, and E(mA) is a lower side current value of the I-P correcting point. IP correction processing is executed on tha basis of a difference between upper side actual pressure ii of the I-P correcting point and an indication pressure and a difference between a lower side actual pressure iii and the indication pressure. Measured precharge time i is measured, and standby pressure stored in an ECU side is vertically corrected according to a difference between the measured precharge time 1 and a reference precharge time stored in advance. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a characteristic correcting device for a proportional electromagnetic control valve, and more particularly to a characteristic correcting device for a proportional electromagnetic control valve of an automatic transmission that executes a characteristic correcting process in accordance with the behavior of a clutch piston.

In hydraulic control of automatic transmissions, instead of using a combination of an accumulator and orifice, the hydraulic pressure from the hydraulic source is directly controlled by a proportional solenoid control valve (linear solenoid), and the friction engagement element (friction clutch, friction A system is known in which the hydraulic pressure supplied to the brake) is controlled to engage / disengage each friction engagement element. In this system, due to the demand for both shortening the speed change operation and preventing the speed change shock, the clutch chamber is rapidly filled with hydraulic oil in the first half of the piston stroke, and the flow rate is gradually reduced in the second half. Therefore, fine control is required to prevent the generation of surge pressure at the stroke end. For example, Japanese Patent No. 3298243 introduces performing quick filling control in a hydraulic control device of an automatic transmission having such an accumulator-less structure.
In order to reliably perform the control, it is required to reduce variations in hydraulic characteristics of the proportional electromagnetic control valve. For example, Japanese Patent Application Laid-Open No. 11-182660 proposes a soretoid characteristic correction device that can compensate by control the adjustment mechanism that is manually adjusted and aligned to the reference value in the line process during manufacturing and assembly. Japanese Patent No. 2919128 and Japanese Patent Laid-Open No. 10-230539 propose a method for correcting a proportional electromagnetic control valve in an injection molding machine. Japanese Patent Application Laid-Open No. 2002-295562 and Utility Model Registration No. 2606138 introduce a technique for eliminating the variation of the proportional electromagnetic control valve by detecting the piston stroke end with a combination of a flow rate detection valve and a hydraulic pressure sensor. Has been.

Japanese Patent No. 3298243, FIG. JP-A-11-182660 Japanese Patent No. 2919128 JP-A-10-230539 JP 2002-295562 A Utility Model Registration No. 2606138

  By the way, in recent years, automatic transmissions are demanding fine control suitable for human sensitivity, especially for the hydraulic control part, more sophisticated and precise control is required, and advanced control can be performed at low cost. The realization is a challenge. Furthermore, in order to realize this at a low cost, it is necessary to achieve the required accuracy of the proportional electromagnetic control valve (linear solenoid) output pressure while maintaining the tact of the production line. In this regard, the above Japanese Patent Laid-Open No. 11-182660, Japanese Patent No. 2919128, and Japanese Patent Laid-Open No. 10-230539 mainly focus on correcting current-voltage characteristics (hereinafter referred to as IP characteristics). The correction of the -P characteristic is not sufficient for the quick filling control of the automatic transmission disclosed in the above-mentioned Japanese Patent No. 3298243. FIG. 20 is a view showing the relationship between the command current and the servo pressure at the time of inspection of the proportional electromagnetic control valve related to the friction brake B1, and (a) shows the case where the piston stroke time becomes maximum, (b) shows This is the case where the piston stroke time is minimized. In FIG. 20A, since the piston stroke is large, naturally the return spring load is large, the piston end pressure is also high, and the oil pressure with respect to the current is low as the IP characteristic. On the other hand, in FIG. 20B, the piston end pressure is low, and the IP characteristic has a high oil pressure with respect to the current. The standard specification is in the middle, but illustration is omitted. FIG. 21 is a diagram showing the relationship between the command current and the servo pressure at the time of inspection of the proportional electromagnetic control valve related to the friction clutch C3. FIG. 21A shows a case where the piston stroke time is maximum, and FIG. This is the case where the piston stroke time is minimized. Considering the correction process of the IP characteristic disclosed in the above-mentioned JP-A-11-182660, JP-A-2919128, and JP-A-10-230539, for example, measurement of at least 2 points is required. However, a point on the low pressure side, for example, a standard current value of 364 mA (498 mA in FIG. 21) corresponding to 150 kPa is supplied to the proportional electromagnetic control valve, and the difference between the actual pressure measurement value and the 150 kPa can be used as a correction value. However, the piston end pressure depends on the clearance of each friction engagement element or the piston stroke management, and is not constant and can be said to be independent of the reference (standard) IP characteristic. Referring again to FIGS. 20 (a) and 21 (a), the point corresponding to 150 kPa is in front of the piston end. Similarly, in FIGS. 20 (b) and 21 (b), the point corresponding to 150 kPa is used. The point is after the end of the piston.

  FIG. 22 (a) shows a quick-fill control for the friction engagement element in the proportional electromagnetic control valve of FIG. 20 (a) with the output shaft on the automatic transmission side free after the IP correction ( The precharge control and the standby pressure control) are carried out, and the command pressure and the actual pressure are plotted. FIG. 22B shows the friction in the proportional electromagnetic control valve shown in FIG. The quick charge control (precharge control and standby pressure control) is performed on the engagement element, and the command pressure and the actual pressure are plotted. In each case, the precharge time is a time obtained by subtracting 20 ms from the time obtained by measurement in advance, the standby pressure is set to a design median value of 135 kpa, and the shelf pressure is set to a value obtained by adding 100 kPa from the standby pressure. When comparing (a) and (b) of FIG. 22, in FIG. 22 (a), the actual pressure reacts with good response after raising from the standby pressure (135 kPa) to the shelf pressure (235 kPa). In FIG. 22B, there is a response delay. FIGS. 23A and 23B are diagrams showing shift waveforms of an actual vehicle by the proportional electromagnetic control valve corresponding to FIGS. 22A and 22B, respectively. When the return spring equivalent pressure in FIG. 23 (a) is high, the set standby pressure becomes higher than the value that should be originally set even if the IP correction is performed. Is too good, resulting in a sense of shock. On the other hand, when the return spring equivalent pressure in FIG. 23B is low, the set standby pressure is lower than the value that should be originally set. The result is lost. Further, as apparent from a comparison between FIGS. 23A and 23B, the output shaft torque waveform is greatly different, so that the sensory result may be greatly different depending on the vehicle or the user. It may also lead to the inability to achieve the goal of stabilizing the quality between models.

  On the other hand, even if the technique introduced in Japanese Patent Application Laid-Open No. 2002-295562 and Utility Model Registration No. 2606138 is used, a flow rate detection valve and a hydraulic sensor are provided in the vicinity of the pressure control valve controlled by each proportional electromagnetic control valve. Each of them must be installed, which not only complicates the hydraulic control device, but also increases the product cost.

  The present invention has been made in view of the above-described circumstances, and an object thereof is a proportional electromagnetic control valve that realizes highly accurate and simple inspection and correction from the viewpoint of stable quality of an automatic transmission. It is an object to provide a characteristic correction apparatus.

  According to a first aspect of the present invention that provides means for solving the above-mentioned problem, the proportional electromagnetic control valve characteristic correction device performs rapid filling control by a combination of predetermined precharge control and standby pressure control. Means for storing and storing a reference precharge time in the event of a failure, means for calculating the actual precharge time until the actual pressure reaches a predetermined threshold by applying the rapid filling control, and the actual precharge time, Means for correcting a standby pressure on the hydraulic control device side according to a difference from the reference precharge time, and the quick filling control at the time of inspection for correcting the IP characteristic of the proportional electromagnetic control valve Based on the difference between the reference precharge time and the measured precharge time, the standby pressure on the hydraulic control device side is corrected without imposing a burden on the production line.

  Also, according to the second aspect of the present invention, the proportional electromagnetic control valve characteristic correction device includes, for each friction engagement element, a reference piston end current value, a reference current value range for piston end detection, and the current. Means for storing and holding the piston end detection condition for specifying the actual pressure reference value within the value range, and gradually increasing the current value for each friction engagement element, the actual pressure value is within the reference piston end current value range. The characteristic value of the proportional electromagnetic control valve on the hydraulic control device side is determined according to the means for detecting the indicated current value at the time when the piston end detection condition is satisfied, and the difference between the indicated current value and the reference piston end current value. And a means for gradually increasing the current value at the time of inspection for correcting the IP characteristic of the proportional electromagnetic control valve, and a difference between the indicated current value and the reference piston end current value. Based in, without burdening the production line, re-corrected I-P characteristic of the proportional electromagnetic control valve.

  Further, according to the third aspect of the present invention, the proportional electromagnetic control valve characteristic correction device includes, for each friction engagement element, a reference piston end current value, a reference current value range for piston end detection, and the current. Means for storing and holding the piston end detection condition for specifying the actual pressure reference value within the value range, and gradually increasing the current value for each friction engagement element, the actual pressure value is within the reference piston end current value range. Means for detecting the indicated pressure at the time when the piston end detection condition is satisfied, and means for correcting the waiting pressure on the hydraulic control device side according to the difference between the indicated pressure and the reference piston end pressure. In the inspection for correcting the IP characteristic of the proportional electromagnetic control valve, control is performed to gradually increase the current value, and a burden is imposed on the production line based on the difference between the indicated pressure and the reference piston end pressure. Call And without correcting the standby pressure of the hydraulic control apparatus.

  In addition, the re-correction processing of the I-P characteristics of the former two proportional electromagnetic control valves is achieved by adopting a stepped hydraulic waveform that increases the current value stepwise at a predetermined step width at predetermined time intervals. It can be performed simply. The former detects the command current value at the time when the command pressure corresponding to the current value exceeds the actual pressure, and according to the difference between the command current value and the reference piston end current value, the hydraulic control device side It is possible to re-correct the characteristic value of the proportional electromagnetic control valve, and the latter detects the command pressure when the command pressure corresponding to the current value exceeds the actual pressure, and the command pressure and the reference The standby pressure on the hydraulic control device side can be corrected according to the difference from the piston end pressure.

  Further, according to the fourth aspect of the present invention, the proportional electromagnetic control valve characteristic correction device stores a reference piston end current value for each friction engagement element and a predetermined value for each friction engagement element. And a means for detecting an indicated current value after a predetermined time from the time of the switching, and a difference between the indicated current value and the reference piston end current value. And means for correcting the characteristic value of the proportional electromagnetic control valve on the hydraulic control device side, and in the inspection for correcting the I-P characteristic of the proportional electromagnetic control valve, when the 0 value of the indicated current value is switched. The standby pressure on the hydraulic control device side is corrected without imposing a burden on the production line based on the indicated current value after a predetermined time and the reference piston end current value.

  Further, according to the fifth aspect of the present invention, the proportional electromagnetic control valve characteristic correction device is configured to store, for each friction engagement element, a means for storing and holding a reference piston end pressure, and for each friction engagement element, a predetermined value. According to the means for detecting the command pressure after a predetermined time from the last command current value of the command current value pattern and detecting the command pressure after the switching, the difference between the command pressure and the reference piston end pressure Means for correcting the standby pressure on the hydraulic control device side, and in the inspection for correcting the IP characteristic of the proportional electromagnetic control valve, the indicated pressure after a predetermined time from when the indicated current value is switched to zero Based on the difference from the reference piston end pressure, the standby pressure on the hydraulic control device side is corrected without imposing a burden on the production line.

  According to the present invention, highly accurate and simple inspection / correction can be performed and stable quality can be maintained without imposing a burden on the inspection line of the automatic transmission.

  Next, the best mode for carrying out the present invention will be described. In the preferable best mode, the present invention executes the standby pressure correction process together with the IP characteristic inspection by the proportional electromagnetic control valve characteristic correction apparatus using the indicated current waveform shown below. FIG. 1 is a schematic diagram showing an example of the relationship between an inspection pattern and an actual pressure and an inspection point in IP characteristic inspection. In the upper part of FIG. 1, the indicated current value A (mA) is 0 value, B (mA) is a precharge pressure equivalent current value, C (mA) is a MAX current value equivalent to the maximum hydraulic pressure value, and D (mA) is IP. The upper current value of the correction point, E (mA) represents the lower current value of the IP correction point, i is the actual precharge time, ii is the upper actual pressure of the IP correction point, and iii is I− It represents the lower actual pressure of the P correction point.

  FIG. 2 is a diagram for explaining the relationship between the actual pressure obtained from the command current waveform of FIG. 1 and the command pressure. The characteristic correcting device for a proportional electromagnetic control valve according to the present embodiment has a difference between the command pressure and the actual pressure (ii and iii in FIG. 1) in the D (mA) section of FIG. 2 and the E (mA) section. While correcting the reference IP, the measured precharge time until the actual pressure reaches a predetermined threshold (i in FIG. 1; preset for each friction engagement element), the friction engagement element The standby pressure stored in the ECU (electronic control unit) of the hydraulic control device is corrected by comparing with the reference precharge time. For example, when the measured precharge time is longer than the reference precharge time, in other words, when the return spring equivalent pressure is high, the standby pressure stored on the ECU side is increased, and the measured precharge time is compared with the reference precharge time. Is short, in other words, when the return spring equivalent pressure is low, the standby pressure stored in the ECU side is reduced.

  As described above, according to the present embodiment, the standby pressure can be corrected together with the IP correction process. This correction content is effective in eliminating the shock feeling when the piston stroke time shown in FIG. 23 (a) is maximum, and when the piston stroke time shown in FIG. 23 (b) is minimum, It is effective to improve the response of the clutch piston and secure a quick feeling by grasping in the torque phase. The standby pressure correction amount is preferably determined by evaluation. However, based on the inspection result, an equation may be derived and corrected by substituting the difference between the measured precharge time and the reference precharge time. good.

Next, a first embodiment of the present invention will be described in detail with reference to the drawings. FIG. 3 is a schematic diagram showing a configuration of a finished product inspection system for an automatic transmission. Referring to FIG. 3, this finished product inspection system is connected to the target automatic transmission 1 via its drive shaft 12 and to the automatic transmission 1 via its output shaft 13. Controlled by a motor 2b, an ECU (electronic control unit) 3 for controlling the automatic transmission 1, and an automatic finished product inspection program incorporated in the ECU (electronic control unit) 3, via a cable 5 and a cable 6. And a sequencer (operating device) 4 for operating the motors 2a and 2b. The automatic transmission 1 includes a position sensor 3 a and is connected to an ECU (electronic control unit) 3 via a sequencer (operating device) 4. Also, in this type of finished product inspection system, filter processing to prevent errors due to hydraulic vibration, and pre-inspection air bleeding processing to suppress the influence of residual air in the oil passage that causes repeated variations are performed. In addition, in order to prevent blunting of the hydraulic pressure, the piping to the hydraulic pressure sensor is made as short as possible and a pressure resistant material is used.

  In this embodiment, although not particularly limited, when the ECU (electronic control unit) 3 and the automatic transmission 1 can be delivered integrally, the delivered ECU (electronic control unit) 3 as shown in FIG. 3 is used. Thus, the result of inspection / correction processing described later can be directly stored in the ECU (electronic control unit) 3. If the above-mentioned integrated delivery is not possible due to the convenience of the delivery destination, etc., an inspection unit corresponding to the ECU (Electronic Control Unit) 3 is used instead of the ECU (Electronic Control Unit) 3, and a storage device (not shown) is described later. The result of the inspection / correction process to be stored can be stored, and the result of the inspection / correction process can be transferred to the separately delivered ECU (Electronic Control Unit) 3 after the automatic transmission 1 is mounted on the vehicle.

  FIG. 4 is a schematic diagram showing a hydraulic control system having a general accumulator-less structure. In FIG. 4, an ECU (electronic control unit) 3 or an inspection unit corresponding thereto includes a characteristic correction device 31 that is executed with a program for executing inspection and correction processing described later, and is necessary for the proportional electromagnetic control valve 23. Control by applying current. The proportional electromagnetic control valve 23 controls the engagement of the clutch 25 by supplying hydraulic oil to the clutch chamber 24 with a clutch pressure via a pressure regulator 22 that regulates the hydraulic pressure from the pump 21 to form a line pressure. It is. With the above configuration, a predetermined test condition (for example, oil temperature 80 ± 10 ° C., input rotation 1500 ± 15 rpm) is set, and proportional electromagnetic control provided in the ECU (electronic control unit) 3 or an inspection unit corresponding thereto. The valve characteristic correcting device 31 is operated to compare the actual pressure from the pressure sensor (not shown) with the command pressure, and execute the IP correction.

FIG. 5 is a diagram for explaining an outline of processing for IP correction using a large number of measurement points. In FIG. 5, a curve Ps is a reference IP characteristic line, and P _{1 ′} , P _{n ′} , and P _{MAX ′} are actually measured IP characteristic lines. A difference between the reference value and the actually measured value is obtained and finally stored in the ECU (electronic control unit) 3. In view of the fact that the IP characteristic line is not a straight line, it can be said that it is preferable to measure a large number of measurement points and perform IP correction based on the measurement points, as shown in FIG. Is determined in consideration of tact and the like on the production line (at least two points above and below).

  FIG. 6 is a diagram for explaining piston end detection conditions used in the present embodiment. The engagement side actual pressure line at the maximum stroke and the engagement side actual pressure line at the minimum stroke shown in FIG. 6 are obtained in advance by evaluation, and the inflection point of these actual pressures (the flow rate control region where the change in hydraulic pressure is gentle) is obtained. A thick straight line connecting the end points is defined as a piston end virtual line. In order to maintain the seal of the clutch piston, the clearance or stroke management of the wet multi-plate clutch and brake of the automatic transmission is always performed to prevent the piston from dropping off. That is, the piston end pressure is defined within a certain range (see FIG. 6), and as a result, the piston end current is also defined (see FIG. 6). In short, in the process of causing the characteristic correction device 31 to perform the above-described IP correction, the point where the actual pressure becomes larger than the virtual line within the piston end current range in FIG. The intersection of the pressure line and the virtual line) is detected as the piston end. In FIG. 6, the imaginary line is described as a straight line connecting two points. For example, the actual pressure line at the minimum stroke, the actual pressure line at the standard stroke, the actual pressure line at the maximum stroke, and the maximum stroke. The engagement side actual pressure line may be obtained by evaluation, and two straight lines connecting these inflection points may be used as the piston end detection condition. For example, a plurality of engagement side actual pressure lines may be evaluated. Of course, the obtained curve may be used as the piston end detection condition.

  The characteristic correction device 31 detects the piston end pressure according to the above-described determination conditions, and based on the differential pressure with the reference piston end pressure separately stored and held, the IP correction content and the standby pressure correction content are The data is output to the storage device of the ECU (electronic control unit) 3 or an inspection unit corresponding thereto. Further, instead of correcting the standby pressure, the reference piston end current value is separately stored and held, and the IP correction content is based on the difference between the reference piston end current value and the detected measured piston end current value. May be corrected again.

  As described above, according to the present embodiment, the piston end is detected together with the IP correction process, and the standby pressure on the ECU (electronic control unit) 3 side is corrected based on the detected piston end. It can be reflected in the P correction result. Of course, the inspection of the piston end may be performed independently of or continuously with the IP correction described above.

  Subsequently, a second embodiment of the present invention will be described. In the above-described first embodiment of the present invention, the example in which the current value (indicated pressure) is increased in an analog manner to detect the piston end has been described. However, in the second embodiment of the present invention, the current value is (Indicating pressure) is stepped up stepwise, the piston end is detected, the standby pressure is corrected, or reflected in the IP correction result. Since the configuration and operation of this embodiment are substantially the same as those of the first embodiment of the present invention, the overlapping portions are omitted, and only the differences will be described.

  FIG. 7 is a diagram for explaining piston end detection conditions in the present embodiment. The solid line in FIG. 7 is a command pressure / actual pressure reference line that represents the relationship between the command pressure obtained by evaluation and the actual pressure, which constitutes the piston end detection condition. It is a figure showing the relationship between the instruction | indication pressure corresponding to the current value of and actual pressure. As is apparent from FIG. 7, when the command pressure is increased at appropriate time intervals, the actual pressure cannot follow during the piston stroke, and therefore the command pressure corresponding to the stepped current value is obtained by evaluation. The indicated pressure / actual pressure is below the reference line. Thereafter, when the piston stroke ends and the piston end is reached, the actual pressure increases rapidly, and a point is obtained that becomes larger than the indicated pressure / actual pressure reference line obtained by the evaluation.

  8 to 11 are diagrams showing an example of an inspection pattern including the present embodiment. In each figure, A is 0 value, B is equivalent to precharge pressure, C is equivalent to maximum hydraulic pressure value (not shown in FIGS. 9 and 10), D is above the IP correction point, and E is IP correction point. The current values on the lower side are respectively shown. As described above, according to the present embodiment, it is possible to easily determine the piston end, and the piston end is detected in series with the IP correction, and based on this, the first of the present invention described above is performed. Similar to the embodiment, the standby pressure on the ECU (electronic control unit) 3 side can be corrected or reflected in the IP correction result. In this embodiment, the inspection pattern is not limited to the inspection patterns illustrated in FIGS. 8 to 11, and the inspection of the piston end and the IP correction described above are independent or continuous. The order of B to E can be changed depending on the influence of hysteresis and the convenience of lines.

  Subsequently, a third embodiment of the present invention will be described. In the first and second embodiments of the present invention described above, the example in which the current value (indicated pressure) is increased to detect the piston end has been described. However, in the third embodiment of the present invention, characteristic correction is performed. The device 31 is used to perform a piston stroke in the reverse direction (from the engaged state to the attached state) even when the current value (indicated pressure) is switched to 0 value together with the IP characteristic correction process, and the piston end is detected. The standby pressure is corrected or reflected in the IP correction result. Since the configuration and operation of this embodiment are substantially the same as those of the first and second embodiments of the present invention, the overlapping portions are omitted, and only the differences are described.

  First, the principle of piston end detection in the present embodiment will be described. FIG. 12 shows the indicated pressure and actual value when switching from A (0 value) to B (equivalent to precharge pressure) and E (below the IP correction point) to A (0 value) in the maximum stroke of the B1 brake. FIG. 13 is a graph in which pressure is plotted, and FIG. 13 shows A (0 value) → B (equivalent to precharge pressure) and E (below the IP correction point) → A (0 value) in the minimum stroke of B1 brake. It is the figure which plotted the indication pressure at the time of switching, and an actual pressure. FIG. 14 shows the indicated pressure and actual value when A (0 value) → B (equivalent to precharge pressure) and E (below the IP correction point) → A (0 value) in the maximum stroke of the C3 clutch. 15 is a graph in which pressure is plotted, and FIG. 15 shows A (0 value) → B (equivalent to precharge pressure) and E (below the IP correction point) → A (0 value) in the minimum stroke of the C3 clutch. It is the figure which plotted the indication pressure at the time of switching, and an actual pressure. Comparing the hydraulic pressure levels considered to be the piston end of the B1 brake and C3 clutch of A (0 value) → B (equivalent to precharge pressure) in FIGS. 12 and 14 and FIGS. 13 and 15, both the B1 brake and the C3 clutch The piston end pressure of the C3 clutch is considerably higher than the piston end pressure of the B1 brake, despite the design of the equivalent pressure of the return spring being the same.

  The reason for the difference is that for the friction engagement element of the brake system, the oil pressure detection position can be installed outside the case from the piston chamber, whereas for the friction engagement element of the clutch system, the seal ring is removed from the piston chamber. This is because the oil pressure is apparently increased because the oil pressure detection position can be taken only in either the case after passing through or the case after passing through the oil pump oil passage. Furthermore, when the oil seal leaks greatly, the flow rate required for the piston stroke is secured, so that the apparent hydraulic pressure is further increased. That is, during the precharge control of A (0 value) → B (equivalent to precharge pressure), the apparent return spring equivalent pressure increases due to piston stroke, oil seal leakage, piston sliding resistance, and the like. Therefore, even if the hydraulic pressure during precharging is detected, it means that the piston end pressure cannot be detected correctly.

  On the other hand, when comparing the hydraulic pressure level considered to be the piston end of E (below the IP correction point) → A (0 value) in FIGS. 12 and 14 and FIGS. 13 and 15, the above A (0 value) → There is no significant difference as much as B (equivalent to precharge pressure). This is because E (below the IP correction point) → A (0 value) starts from the piston end state, and the piston stroke is not performed. This is because the residual pressure of the piston and the return spring equivalent pressure are almost balanced.

  FIGS. 16 to 19 correspond to FIGS. 12 to 15, respectively, with time-hydraulic waveform (solid line) and IP characteristics (E (below the IP correction point) → A (0 value)) FIG. Since the IP characteristic causes the current to rise or fall relatively slowly, the point considered to be the piston end between piston strokes appears in the time-hydraulic waveform (solid line) in a state of being deviated from the IP line. It can be read as a value approximately equal to the end pressure.

  As shown in FIGS. 16 and 17, the piston end pressure read from the time hydraulic waveform (solid line) of the B1 brake is equal to or slightly lower than the piston end pressure of IP, and there is no practical problem. The piston end pressure read from the time oil pressure waveform (solid line) of the C3 clutch is lower than the piston end pressure of IP both at the maximum and minimum strokes. As described above, the C3 clutch is configured to reach the oil pressure detection position from the piston chamber through the seal ring due to the influence of leakage of the seal ring. This is because the pressure is lower than the return spring equivalent pressure. However, in the inspection in the line process, the temperature can be set in a very narrow range such as 80 ± 10 ° C. and the inspection can be performed. it can.

  As described above, the characteristic correction device 31 is used to detect the oil pressure at the inflection point of the oil pressure that seems to be the piston end pressure of E (below the IP correction point) → A (0 value). The pressure can be detected. For example, the actual pressure value is 25 msec after the command current is switched from E (below the IP correction point) to A (0 value) (when the cycle time is 5 msec, the hydraulic pressure at the fifth cycle is detected). Can be detected as the piston end pressure. Then, the characteristic correction device 31 may be used to increase or decrease the standby pressure as described in the above embodiments based on the difference between the piston end pressure and the reference piston end pressure. Based on the corresponding current value, for example, the re-correction of IP may be performed so that the piston end design value 135 kPa becomes the same current value.

It is the schematic diagram showing the inspection pattern and inspection point in IP characteristic inspection of one Embodiment of this invention. It is a figure for demonstrating the relationship between the actual pressure obtained by the test | inspection of FIG. 1, and a command pressure. It is the schematic diagram which showed the structure of the finished product inspection system of an automatic transmission. It is the schematic diagram which showed the hydraulic control system of the accumulator-less structure. It is a figure for demonstrating the process outline | summary of IP correction | amendment. It is a figure for demonstrating piston end detection conditions. It is another figure for demonstrating piston end detection conditions. It is a figure showing an example of the test | inspection pattern of the 2nd Example of this invention. It is a figure showing another example of the test | inspection pattern of the 2nd Example of this invention. It is a figure showing another example of the test | inspection pattern of the 2nd Example of this invention. It is a figure showing another example of the test | inspection pattern of the 2nd Example of this invention. It is a figure for demonstrating the principle of the 3rd Example of this invention. It is a figure for demonstrating the principle of the 3rd Example of this invention. It is a figure for demonstrating the principle of the 3rd Example of this invention. It is a figure for demonstrating the principle of the 3rd Example of this invention. It is a figure for demonstrating the 3rd Example of this invention. It is a figure for demonstrating the 3rd Example of this invention. It is a figure for demonstrating the 3rd Example of this invention. It is a figure for demonstrating the 3rd Example of this invention. It is a figure showing the relationship between instruction | indication electric current and servo pressure, (a) is a case where piston stroke time becomes the maximum, (b) is a case where piston stroke time becomes the minimum. It is another figure showing the relationship between instruction | indication electric current and servo pressure, (a) is a case where piston stroke time becomes the maximum, (b) is a case where piston stroke time becomes the minimum. It is the figure which implemented rapid filling control after IP correction | amendment, and plotted the command pressure and the actual pressure, (a) is the case where piston stroke time becomes the maximum, (b) is the piston stroke time minimum This is the case. It is a figure showing the shift waveform in a real car after IP amendment, (a) is a case where piston stroke time becomes the maximum, and (b) is a case where piston stroke time becomes the minimum.

Explanation of symbols

1 Automatic transmission 2a, 2b Motor (operating device)
3 ECU (Electronic Control Unit)
4 Sequencer (operating device)
5, 6 Cable 12 Drive shaft 13 Output shaft 21 Pump 22 Pressure regulator 23 Proportional electromagnetic control valve 24 Clutch chamber 25 Clutch 31 Characteristic correction device

Claims (7)

A proportional electromagnetic control valve characteristic correction device provided in a hydraulic control device of an automatic transmission that controls engagement / disengagement of a friction engagement element using a proportional electromagnetic control valve that operates a piston,
Means for storing and storing a reference precharge time when performing quick filling control by a set of predetermined precharge control and standby pressure control for each friction engagement element;
Means for applying the quick filling control for each friction engagement element and calculating an actual precharge time until the actual pressure reaches a predetermined threshold;
Means for correcting the standby pressure on the hydraulic control device side according to the difference between the measured precharge time and the reference precharge time;
A characteristic correction device for a proportional electromagnetic control valve. A proportional electromagnetic control valve characteristic correction device provided in a hydraulic control device of an automatic transmission that controls engagement / disengagement of a friction engagement element using a proportional electromagnetic control valve that operates a piston,
A means for storing and holding a reference piston end current value, a reference current value range for piston end detection, and a piston end detection condition for specifying an actual pressure reference value within the current value range for each friction engagement element;
Means for gradually increasing the current value for each friction engagement element to detect an indicated current value at a time when the actual pressure value satisfies the piston end detection condition within the reference piston end current value range;
Means for correcting a characteristic value of the proportional electromagnetic control valve on the hydraulic control device side according to a difference between the indicated current value and the reference piston end current value;
A characteristic correction device for a proportional electromagnetic control valve. A proportional electromagnetic control valve characteristic correction device provided in a hydraulic control device of an automatic transmission that controls engagement / disengagement of a friction engagement element using a proportional electromagnetic control valve that operates a piston,
A means for storing and holding a reference piston end pressure, a reference current value range for piston end detection, and a piston end detection condition for specifying an actual pressure reference value within the current value range for each friction engagement element;
Means for gradually increasing a current value for each friction engagement element, and detecting an indicated pressure when an actual pressure value satisfies the piston end detection condition within the reference piston end current value range;
Means for correcting a standby pressure on the hydraulic control device side according to a difference between the command pressure and the reference piston end pressure;
A characteristic correction device for a proportional electromagnetic control valve. A proportional electromagnetic control valve characteristic correction device provided in a hydraulic control device of an automatic transmission that controls engagement / disengagement of a friction engagement element using a proportional electromagnetic control valve that operates a piston,
Means for storing and holding a reference piston end current value for each friction engagement element;
For each friction engagement element, the current value is increased stepwise with a predetermined step width at predetermined time intervals, and the indicated current value when the indicated pressure corresponding to the current value exceeds the actual pressure is detected. Means to
Means for correcting a characteristic value of the proportional electromagnetic control valve on the hydraulic control device side according to a difference between the indicated current value and the reference piston end current value;
A characteristic correction device for a proportional electromagnetic control valve. A proportional electromagnetic control valve characteristic correction device provided in a hydraulic control device of an automatic transmission that controls engagement / disengagement of a friction engagement element using a proportional electromagnetic control valve that operates a piston,
Means for storing and retaining a reference piston end pressure for each friction engagement element;
For each friction engagement element, the current value is increased stepwise with a predetermined step width at predetermined time intervals, and the indicated pressure when the indicated pressure corresponding to the current value exceeds the actual pressure is detected. Means,
Means for correcting a standby pressure on the hydraulic control device side according to a difference between the command pressure and the reference piston end pressure;
A characteristic correction device for a proportional electromagnetic control valve. A proportional electromagnetic control valve characteristic correction device provided in a hydraulic control device of an automatic transmission that controls engagement / disengagement of a friction engagement element using a proportional electromagnetic control valve that operates a piston,
Means for storing and holding a reference piston end current value for each friction engagement element;
Means for switching from the last command current value of a predetermined command current value pattern to a zero value for each friction engagement element, and detecting a command current value after a predetermined time from the switching time;
Means for correcting a characteristic value of the proportional electromagnetic control valve on the hydraulic control device side according to a difference between the indicated current value and the reference piston end current value;
A characteristic correction device for a proportional electromagnetic control valve. A proportional electromagnetic control valve characteristic correction device provided in a hydraulic control device of an automatic transmission that controls engagement / disengagement of a friction engagement element using a proportional electromagnetic control valve that operates a piston,
Means for storing and retaining a reference piston end pressure for each friction engagement element;
Means for switching from the last command current value of a predetermined command current value pattern to a zero value for each friction engagement element, and detecting the command pressure after a predetermined time from the switching time;
Means for correcting a standby pressure on the hydraulic control device side according to a difference between the command pressure and the reference piston end pressure;
A characteristic correction device for a proportional electromagnetic control valve.

Images