JP2008111475A - Electromagnetic control valve device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an electromagnetic control valve device having a configuration suitable for controlling a pressure fluctuation of hydraulic oil in an electronic controlled hydraulic brake device from high pressure to low pressure with a small amount of flow to give linear motion to a valve element with electromagnetic force, thus actualizing continuous pressure control while stabilizing the operation of the valve element in all pressure ranges. <P>SOLUTION: The electromagnetic control valve device comprises an electromagnetic force generating means 11, the valve element 14 to be moved with electromagnetic force, a seat portion 15 provided on the upper side of the valve element, and an elastic body 16 for energizing the valve element to be pushed against the seat portion. In the case where a current value required for separating the valve element from the seat portion is set to be a maximum working current when fluid has no pressure difference between a time before passing between the valve element and the seat portion and a time after that, the elastic body 16 has a load change rate which is positively and negatively opposite to and same in size as the change rate of the electromagnetic force to the displacement of the valve element when the maximum working current is applied to the electromagnetic force generating means 11 in the range of displacement (effective displacement) of the valve element where a flow amount passing between the valve element 14 and the seat portion 15 is changed with the movement of the valve element 14. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an electromagnetic control valve device, and particularly to a device in which the pressure changes greatly from a high pressure to a low pressure at a small flow rate, such as an electronically controlled hydraulic brake device for a vehicle, while maintaining the continuity of hydraulic oil pressure change. The present invention relates to an electromagnetic control valve device suitable for pressure control.

  In recent years, hydraulic brake devices for vehicles have a side-slip prevention function by independently controlling the braking force of each wheel, and a braking force control by precisely controlling the hydraulic pressure, such as cooperative control with a regenerative brake of a hybrid vehicle. The demand for is increasing.

  The brake fluid pressure is generally controlled by an electromagnetic control valve device. In this type of hydraulic brake device, an electromagnetic control valve having a simple structure and a low cost using a solenoid as described in Patent Document 1 or Patent Document 2 is used. Conventionally, a valve that is controlled by a binary value of full open / close of a valve by turning on and off a current applied to a coil as described in Patent Document 1 has been used. However, in recent years, due to the demand for precise braking force control as described above, Patent Document 2 and the like have been replaced with a control valve that can control the position of the valve body according to the magnitude of the applied current and can continuously control the pressure. is there.

  If the continuity of pressure control by the electromagnetic control valve device for continuous control of pressure for such a hydraulic brake device is impaired due to any cause, the controllability of the control force may be impaired There is. Therefore, the controllability is improved by devising the magnetic circuit by changing the shape or by taking a large suction gap to reduce the change in electromagnetic force accompanying the displacement of the valve body.

Further, there is an electromagnetic control valve device having a structure similar to that of Patent Document 2 described in Patent Document 3 as a technique for removing a change in electromagnetic force due to valve body displacement. An electromagnetic control valve device used in a hot water supply device or the like is characterized by including an elastic body whose spring constant changes due to displacement. That is, by changing the spring constant, the change characteristic of the attractive force with respect to the displacement of the electromagnetic force with respect to the valve body is canceled, and the controllability of the flow rate by the electromagnetic control valve device is improved.
Japanese Patent Laid-Open No. 6-312653 JP-A-10-315946 JP-A-7-217766

  In order to realize accurate braking force control, it is necessary to continuously control from high pressure to low pressure in an electromagnetic control valve device used in an electronically controlled hydraulic brake device. However, in the case of the conventional control valve, when the fluid pressure difference is small before and after passing between the valve body and the seat part, the operation of the valve body becomes unstable, and the continuity of the pressure change is impaired. High braking force control may not be possible.

  In the method described in Patent Document 3, it is necessary to use a spring having a non-linear characteristic with respect to the displacement, so that there is a possibility that the electromagnetic control valve device becomes large due to an increase in cost and an increase in the spring. .

  Further, in the brake device, the amount of fluid moving in the pipe is small, but there is a large change in fluid pressure. Therefore, it is necessary to control the valve body position within a minute range. Furthermore, a small solenoid valve has a feature that it has a large suction gap in order to reduce changes in electromagnetic force with respect to the valve body displacement. Since the rate of change of the electromagnetic force characteristics varies depending on the applied current value and valve body displacement, it is difficult to realize a spring having non-linear characteristics that can realize a spring constant in consideration of all states.

  The present invention has a configuration in which the valve body is directly moved by electromagnetic force, which is suitable for controlling a change in hydraulic oil pressure from a high pressure to a low pressure with a small flow rate such as an electronically controlled hydraulic brake device having a simple structure and a small size. An object of the electromagnetic control valve device is to provide an electromagnetic control valve device capable of stabilizing the valve body operation in the entire pressure range and realizing continuous pressure control.

In order to achieve the above object, the present invention mainly adopts the following configuration.
Current control means for calculating and outputting a current value corresponding to the target control amount, electromagnetic force generation means for changing the electromagnetic force generated by the applied current value, and movement by the electromagnetic force generated by the electromagnetic force generation means In an electromagnetic control valve device comprising: a valve body that is configured to seat, a seat portion that is disposed so as to face the valve body, and an elastic body that biases the valve body, the valve body and the seat portion When there is no pressure difference between the fluid before and after passing between the valve body and the current value necessary for separating the valve body from the seat portion is the maximum working current, the valve body is interlocked with the movement of the valve body. When the maximum operating current is applied to the electromagnetic force generating means within the range of displacement of the valve body in which the flow rate of the fluid passing between the body and the seat portion changes, the electromagnetic force with respect to the displacement of the valve body Force change rate and positive / negative are opposite and the same magnitude A structure comprising the elastic body having a load change rate.

  Further, in the electromagnetic control valve device, the elastic body has a rate of change of electromagnetic force with respect to the displacement of the valve body when the electromagnetic force change characteristic is linearly approximated within the range of displacement of the valve body. The structure is an elastic body having a linear characteristic that is opposite to the positive and negative and has the same rate of load change. Furthermore, in the electromagnetic control valve device, the elastic body is arranged to be urged in a direction in which the valve body is pressed against the seat portion. Further, in the electromagnetic control valve device, the pressure difference of the fluid before and after passing between the valve body and the seat portion is replaced with 1 / of the maximum pressure applied to the valve body instead of when there is no pressure difference. When the current required for starting the valve body is a low-voltage required current when the pressure is 4 or less, the flow rate passing between the valve body and the seat portion changes in conjunction with the movement of the valve body. Within the range of displacement of the valve body, when the low-voltage required current is applied to the electromagnetic force generating means, the rate of change relative to the displacement when linearly approximating the change characteristics of the electromagnetic force relative to the displacement of the valve body; The structure is provided with the elastic body having a linear characteristic that is opposite in polarity and has a load change rate of the same magnitude. Further, in the electromagnetic control valve device, a range smaller than a range of displacement of the valve body in which a flow rate of a fluid passing between the valve body and the seat portion changes in conjunction with the movement of the valve body. A configuration in which the elastic body has a load change rate of the same magnitude as the rate of change of the electromagnetic force with respect to the displacement of the valve body, but opposite in polarity when the maximum operating current is applied to the electromagnetic force generating means. And

  According to the present invention, in a predetermined valve body displacement range and a current value applied to a predetermined electromagnetic force generating means, a linear characteristic in which a load change rate is set so as to cancel the change of the electromagnetic force characteristic with respect to the valve body displacement. Use elastic body. As a result, it is possible to realize pressure control that stabilizes the valve body operation and maintains the continuity of the pressure change with a simple structure and a small device. As a result, an electronically controlled hydraulic brake device with high controllability can be realized at low cost.

  The electromagnetic control valve device according to the first and second embodiments of the present invention will be described below with reference to FIGS.

  A best mode for carrying out the present invention will be described based on a first embodiment. FIG. 1 is a schematic cross-sectional view of an electromagnetic control valve device 10 used in a hydraulic brake device according to a first embodiment of the present invention. In the electromagnetic control valve device according to the first embodiment, an electromagnetic force is generated by the electromagnetic force generating means 11 using a coil, and the force acts in the direction attracted to the suction surface of the core 12 by the electromagnetic force, thereby causing the inside of the cylinder 13 to move. The valve body 14 moves. Further, the first embodiment includes a seat portion 15 that is provided below the FIG. 1 and adjusts the flow rate that passes through the electromagnetic control valve device 10 according to the distance from the valve body 14. Further, the valve body 14 is urged by an elastic body 16, and in the case of the electromagnetic control valve device 10 having the configuration as shown in FIG. 1, the valve body 14 is seated in a state where no current is supplied to the electromagnetic force generating means 11. 15 is pressed.

  Further, a high-pressure part is connected to the lower side of the seat part 15 in FIG. 1, and a reservoir and a pressurizing object are connected to the outlet side. A driver circuit 17 and a controller 18 are connected to the electromagnetic force generating means 11. The controller 18 calculates hydraulic fluid pressure that can generate a target braking force based on information from various sensors 19 that detect the hydraulic pressure of the brake device, the amount of brake operation by the driver, the amount of vehicle movement, and the like, and outputs a command value to the driver circuit 17. calculate. The magnitude of the electromagnetic force of the electromagnetic force generating means 11 is determined by the magnitude of the current value from the driver circuit 17. The position where the electromagnetic force and the load due to the elastic body 16 and the force due to the pressure from below in FIG. In the electromagnetic control valve device targeted in the first embodiment, the gap 20 (the movable range of the valve body 14 with respect to the core 12) is set large in order to improve the controllability of the position of the valve body 14.

  In the first embodiment of the present invention, in the electromagnetic control valve device 10 having the above-described configuration, a load having a value obtained from the relationship between the electromagnetic force of the electromagnetic force generating means 11 and the displacement of the valve body 14 obtained in advance by measurement or calculation. An elastic body 16 having a rate of change, that is, a spring constant is selected and used. Specific functions and operation modes of the electromagnetic control valve device according to the first embodiment will be described below with reference to FIG. FIG. 2 is a diagram illustrating the relationship between the electromagnetic force and the valve body displacement and the effective displacement in the electromagnetic force generating means according to the first embodiment.

  Like the flow rate and the displacement of the valve body 14 shown in the lower diagram of FIG. This effective displacement corresponds to a range in which the flow path area A2 formed by the valve element 14 being separated from the seat part 15 is smaller than the flow path area A1 of the seat part 15, and this effective displacement is the maximum displacement equal to the gap 20. Smaller than the amount.

  The spring constant of the elastic body 16 is determined so as to cancel the change of the electromagnetic force with respect to the displacement of the valve body 14 in the displacement range smaller than the effective displacement with the electromagnetic force characteristics as shown in the upper diagram of FIG. Here, the displacement and force are positive in the direction away from the seat portion. Further, as shown in the upper diagram of FIG. 2, the electromagnetic force characteristics tend to increase as the current value increases with respect to the displacement of the valve body 14. That is, change in C1> change in C3.

  As a matter of course, when the current applied to the electromagnetic force generating means (coil) shown in FIG. 1 is increased, the electromagnetic force is increased accordingly, and the displacement amount of the valve body is increased. The flow path area of the control valve 10 also increases within the range of displacement. Furthermore, the pressure difference between the hydraulic fluid applied to the valve body 14 before and after the flow path between the valve body and the seat portion (for example, brake fluid) is applied in the direction separating the valve body from the seat portion. Even with the valve body displacement amount (appropriate displacement Xi within the effective displacement range in FIG. 2), it is necessary to apply a larger current to the coil when the pressure difference is small than when the pressure difference is large.

  Therefore, the electromagnetic force when the pressure difference of the hydraulic fluid is small before and after passing through the valve body 14 and the seat portion 15 (a larger current value is required than the large pressure difference in order to operate the valve body 14). The spring constant of the elastic body 16 is determined so as to correct the characteristic. Here, as the current value required to separate the valve element 14 from the seat portion 15 when the largest current is required and there is no pressure difference, the electromagnetic force characteristic when applied to the electromagnetic force generating means 11 is used. It is assumed that the curve is represented by C2 (when the electromagnetic force C2 is generated, the valve body can be moved to the maximum effective displacement when there is no pressure difference of the hydraulic fluid).

  FIG. 3 is a diagram illustrating a correction function of the electromagnetic force characteristic (see the upper diagram of FIG. 2) according to the spring constant of the elastic body according to the first embodiment. FIG. 3A is an enlarged view of C2 in FIG. 2 within the effective displacement range. Here, as indicated by a broken line, the rate of change of the electromagnetic force F with respect to the displacement 14 of the valve body 14 when the curve (solid line) is approximated by a straight line is ΔF / Δx. At this time, in the first embodiment, the spring has a spring constant such that the load change of the spring has the characteristics shown in FIG. That is, if the elastic body 16 spring constant is K, the characteristic of K = −ΔF / Δx is set so that the rate of change when the electromagnetic force characteristic indicated by C2 is approximated by a straight line and the change in polarity are opposite. It is assumed to have a spring. FIG. 3 (c) shows the absolute value of the resultant force obtained by adding the electromagnetic force characteristics of FIG. 3 (a) and the load characteristics of the elastic body of FIG. 3 (b) in such a state. In this way, if the spring constant is determined in consideration of the balance with the electromagnetic force when there is no differential liquid pressure difference, even if the pressure difference becomes high, the spring constant can be set by setting this spring constant. Operation is not unstable.

  As described above, by setting the spring constant of the elastic body 16 having linear characteristics, it is possible to reduce the change of the force obtained by adding the electromagnetic force F and the load FS of the elastic body 16 with respect to the displacement of the valve body 14. it can. At this time, the range of displacement (effective displacement shown in FIG. 2) for correcting the electromagnetic force characteristics is made smaller than the maximum displacement of the valve body 14 (see FIG. 2). By the correction, the change of the electromagnetic force relative to the displacement of the valve body 14 can be made sufficiently small. The electromagnetic control valve device 10 having the above-described configuration can realize pressure control by continuous pressure change even when used in an environment where the pressure fluctuation of the brake fluid is large. In other words, since the condition of the spring constant is set when there is no pressure difference of the brake fluid, it is sufficiently applicable even when the pressure difference increases. Incidentally, the condition setting of the elastic body in the prior art is that the valve is closed against the brake fluid pressure from below shown in FIG. 1 when the current applied to the coil is zero.

  Here, as shown in the upper diagram of FIG. 4, a current is input into the electromagnetic control valve device 10 in a ramp shape (a proportional input is applied), and the pressure is applied to the low pressure side (reservoir) from the accumulated brake caliper. The operation of the electromagnetic control valve device will be described assuming the case of escape. FIG. 4 is a diagram showing valve body displacement and inlet pressure change with respect to a ramp-like current input in a conventional electromagnetic control valve device. According to the middle diagram of FIG. 4, when the applied current is increased to shift the valve body displacement in the opening direction, the electromagnetic force increases due to the valve body displacement at a certain displacement position as shown in the upper diagram of FIG. As a result, the valve body displacement position becomes unstable and moves up and down, making it difficult to control the position of the valve body displacement.

  The lower diagram of FIG. 4 shows the pressure change at the inlet of the electromagnetic control valve device 10 to which the first embodiment is not applied. When the pressure at the inlet becomes low, the pressure continuously changing until then shows a discontinuous change. This discontinuous change is that when the pressure becomes low, the pressure difference between the hydraulic fluid before and after passing between the valve body 14 and the seat portion 15 becomes small, and the force that pushes up the valve body 14 from below in FIG. This is because, in the state, the ratio of the electromagnetic force out of the force acting on the valve body 14 is increased, and the influence of the change in the electromagnetic force characteristics is greatly affected. Further, at this time, the current value necessary for operating the valve body 14 also becomes large (because it is close to the assumed C2 as described above), so that the electromagnetic force valve body 14 as shown in FIG. The rate of change with respect to displacement is greater.

  In addition, the absolute value of the resultant force between the suction electromagnetic force and the load of the elastic body 16 when the pressure difference is small and the absolute value of the force (pressure difference × pressure receiving area + fluid force) caused by the fluid passing through the electromagnetic control valve device 10 are shown. The result is as shown in FIG. Here, FIG. 5 is a diagram showing the relationship between the absolute value of the resultant force of the electromagnetic force and the elastic body load when the pressure difference is large and when the pressure difference is small, and the force caused by the passing fluid in the electromagnetic control valve device of the prior art. It is.

  When the differential pressure is large as shown in FIG. 5A, the intersection of the two curves is an independent point, and in this case, the valve body operation is stabilized. However, when the pressure difference is small as shown in FIG. 5B, a part of the curve of the resultant force of the electromagnetic force and the elastic body load partially overlaps the curve of the force due to the fluid. In this case, there is a high possibility that the position of the valve body 14 will be indefinite, and the valve body operation may become unstable. Here, in FIG. 5B, the solid line curve decreases with the magnitude of the valve element displacement x in contrast to FIG. 5A, as described above, in the valve element 14 when the pressure difference is small. This is because the ratio of electromagnetic force among working forces increases. It should be noted that the elastic body load in the prior art is designed from the viewpoint of being closed in balance with the brake fluid pressure from below shown in FIG. 1 when the applied current is zero. Incidentally, the elastic body load of FIG. 7B showing the first embodiment is somewhat larger than that of FIG. 5B.

  On the other hand, the absolute value of the resultant force of the electromagnetic force and the elastic body 16 load when the spring constant of the elastic body 16 is determined by applying the first embodiment of the present invention is shown in FIG. Here, the electromagnetic force characteristics shown in FIG. 2 are also indicated by broken lines. As described above, if the elastic body 16 having a linear change characteristic of the spring constant that flattens the curve C2 is used, the resultant force shown by the solid lines C1 'to C3' is obtained. As shown here, the force of C2 'hardly changes with the displacement of the valve body 14. FIG. 7 shows the absolute value of the resultant force of the force by the fluid acting on the valve body 14 and the electromagnetic force and the load of the elastic body 16 as in FIG.

  As shown in FIG. 7, in the case of a small pressure difference (FIG. 7B), the curve change rate of the absolute value of the resultant force of the electromagnetic force and the elastic body 16 load becomes small. The operation of the valve body 16 becomes stable. Further, the electromagnetic force characteristics when the current is low, here, C3 becomes a curve with a downward slope like C3 'by this correction (see FIG. 6). For this reason, in the case of a large pressure difference (FIG. 7A), the absolute value of the resultant force of the electromagnetic force and the load by the elastic body 16 has a characteristic of rising to the right. In this case, as is apparent from the drawing, the stability of the operation of the valve body 14 is not impaired as much as it rises to the right. Further, although the current value necessary for the operation of the valve body 14 when the pressure difference is large slightly increases, the maximum current value of the electromagnetic control valve device is corrected because the electromagnetic force characteristic when the maximum current value is applied is corrected. There is an advantage that the value does not change. Also, C1 becomes C1 'by the correction, and the electromagnetic force characteristic increases to the right. However, this portion is not relevant because pressure control by the electromagnetic control valve device of this system is not performed.

  For the electromagnetic control valve device 10 according to the first embodiment using the elastic body 16 subjected to the correction as described above, the pressure change when a current is input in a ramp shape as in FIG. 4 is shown in FIG. To express. In FIG. 8, the dotted line indicates the pressure change when the present invention is not applied, as in FIG. 4, and the solid line indicates the pressure change when the first embodiment is applied. As shown here, when Example 1 is applied, there is no sudden change in pressure regardless of whether the pressure is high or low, and a continuous pressure change can be realized. Therefore, the controllability of the pressure is improved, the braking force control with high accuracy using the electromagnetic control valve device 10 can be realized, and the cooperation with the precise vehicle motion control and the regenerative brake can be realized. Further, since the electromagnetic force characteristic is corrected by the elastic body 16 having a linear characteristic, a small and low-cost device can be realized.

  Further, almost the same effect is obtained when the spring constant of the elastic body 16 is determined when the pressure difference is equal to or less than ¼ of the maximum pressure applied to the electromagnetic control valve (in the above description, the pressure difference is zero). However, when there is a slight pressure difference, when the pressure is about 1/4 of the maximum pressure (under a considerably small pressure), the current value necessary to separate the valve body from the seat portion 15 When the electromagnetic force is applied to the electromagnetic force generating means 11, the rate of change of the electromagnetic force with respect to the displacement of the valve body 16 and the positive and negative values are reversed and have the same magnitude. Here, ¼ indicates that the maximum pressure applied to the high pressure side of the electromagnetic control valve device such as a brake device is about 3 to 5 MPa when the maximum pressure is about 15 to 20 MPa. That is, by correcting the valve body operation so that it becomes stable when the valve body operation starts to become unstable, the subsequent operation is prevented from becoming unstable.

  Further, the displacement of the valve body when controlling the pressure is within a small range (smaller than the displacement from the valve body displacement 0 to the effective displacement) than the range of displacement in which the flow path area can be changed (the effective displacement range shown in FIG. 2). In the range up to the displacement of the valve body), the same effect can be obtained by determining the spring constant of the elastic body 16 so as to cancel the change characteristic of the electromagnetic force with respect to the displacement of the valve body in that range. can get.

  Further, as shown in FIG. 9, an electromagnetic force characteristic correcting elastic body 111 different from the elastic body 16 that urges the valve body 14 and presses the valve body 14 against the seat portion without applying an electric current is provided. In this case as well, the electromagnetic force generated by the electromagnetic force generating means 11 and the load of the elastic body 16 are within the range of the displacement of the valve body 14 where the flow rate changes due to the displacement of the valve body 14 in substantially the same manner as shown in FIG. Even if the electromagnetic force characteristic correcting elastic body 111 having a spring constant that cancels the change of the resultant force with respect to the valve body displacement is used, the same effect can be obtained. In other words, the function shown in FIG. 3B is obtained by combining the spring 16 that opposes the hydraulic oil pressure from the bottom shown in FIG. 1 of the prior art (when the applied current is zero) and the elastic body 111 for electromagnetic force characteristic correction. Is played.

  An electromagnetic control valve device according to Embodiment 2 of the present invention will be described in detail with reference to FIG. FIG. 10 is an electromagnetic control valve device according to a second embodiment of the present invention, and is an overall configuration diagram of an electronically controlled hydraulic brake device using the configuration of the first embodiment. In the following, in FIG. 10, only the configuration different from that in FIG. 1 will be described, and the same configuration as in FIG.

  The configuration shown in FIG. 10 corresponds to one wheel of an electronically controlled hydraulic brake device. The electromagnetic control valve devices 10 and 201 (same configuration as the reference numeral 10) described in the first embodiment are arranged between the pump 202 and the brake caliper 203, and between the brake caliper 203 and the reservoir 204, and each is hydraulic piping. Connect at 206. The pump 202 is controlled by a pump controller 207, and a pressure sensor 208 for detecting the pressure is provided.

  In the electronically controlled hydraulic brake device having the configuration as shown in FIG. 10, the pump 202 is controlled by the pump controller 207 and the hydraulic fluid is sent out from the reservoir 204. Then, by driving the electromagnetic control valve device 10, the pressure of the brake caliper 203 is increased, and a braking force is generated by pressing the brake pad against the brake disc by the piston. Further, the electromagnetic control valve device 10 is closed and the other electromagnetic control valve device 201 is driven to release the hydraulic fluid from the brake caliper 203 to the reservoir 204, thereby reducing the pressure applied to the piston and releasing the braking.

  In the electronically controlled hydraulic brake device shown in FIG. 10, when the electromagnetic control valve device (the elastic body having the function of FIG. 3) of the first embodiment is used, a continuous change in pressure is guaranteed. Without providing a detection means in front of the caliper 203, it is possible to predict the oil pressure applied to the piston.

  Next, the operation and function of the second embodiment shown in FIG. 10 will be specifically described. Only the pressure before the electromagnetic control valve device 10 is measured by the pressure sensor 208. The relationship between the applied current to the electromagnetic control valve devices 10 and 201, the differential pressure and the pressure change over time is calculated or measured in advance. When the time change of the pressure of the electromagnetic control valve device 10 is ΔP and the pressure applied to the piston before driving the electromagnetic control valve device 10 is P1, the pressure P1 applied to the piston after t seconds is P1 = ΔP · t + P0. At this time, ΔP is determined by the applied current and the differential pressure. Since the electromagnetic control valve device 10 according to the second embodiment can continuously control the pressure, the error is reduced even when the pressure is estimated by the above-described operation and method.

  Further, when the electromagnetic control valve device 201 is driven to release the braking, the pressure applied to the piston can be estimated in the same manner. By using this, the accuracy of the feedforward control of the braking force can be improved, and the response time can be shortened.

  As described above, in order to solve the following problems, the embodiment of the present invention is characterized by having the following configuration and having functions or actions. That is, the pressure of the hydraulic fluid (brake fluid) changes suddenly and the continuity of the pressure change is impaired because the operation of the valve body becomes unstable when the pressure difference between the valve body and the seat portion is small. Because there is. That is, when the pressure difference is small, the force acting on the valve body is smaller than that of the brake fluid, and the ratio of the electromagnetic force out of the force acting on the valve body is increased, so that it is easily affected by changes in the electromagnetic force. In the case of an electromagnetic control valve device in which the valve body is directly moved by the electromagnetic force taken up in the embodiment of the present invention, the electromagnetic force changes with respect to the valve body displacement. Prone to instability. Furthermore, since the electromagnetic force changes with respect to the displacement, there are multiple valve body positions in close displacement where the force acting on the valve body is balanced when the pressure difference is small, so the valve body position becomes unstable and unstable. It is easy to become.

  Therefore, the electromagnetic control valve device of the present embodiment calculates and outputs a current value corresponding to the target control amount, an electromagnetic force generating means that changes the electromagnetic force generated by the applied current value, An electromagnetic control valve comprising: a valve body that is moved by electromagnetic force generated by the electromagnetic force generating means; a seat portion that is installed so as to face the valve body; and an elastic body that is urged against the valve body. In the apparatus, when there is no pressure difference in the fluid before and after passing between the valve body and the seat portion, when the current value necessary to separate the valve body from the seat portion is the maximum use current, The valve when the maximum operating current is applied to the electromagnetic force generating means within a range of displacement of the valve body in which a flow rate passing between the valve body and the seat portion is changed by movement of the valve body. Rate of change of electromagnetic force against body displacement And having the elastic body sign has the same size load change rate in the reverse.

  According to the present embodiment, the electromagnetic force and the elasticity are set by setting the load by the elastic body biased to the valve body to be opposite to the change in the magnitude of the electromagnetic force accompanying the displacement of the valve body. The force obtained by adding the body load can be prevented from changing with respect to the displacement of the valve body, so that the valve body operation can be stabilized, and pressure control can be performed without impairing the continuity of the pressure change. Further, when determining the characteristics of the electromagnetic force to be corrected with respect to the displacement of the valve body, it is possible to realize stabilization of the valve body operation regardless of the magnitude of the pressure difference with a simple structure. Cost can be maintained.

  In the electromagnetic control valve device, the elastic body that urges the valve body may change a flow rate that passes between the valve body and the seat portion due to the movement of the valve body. This is an elastic body with linear characteristics that has the same rate of load change rate as the rate of change with respect to the displacement of the valve body when the electromagnetic force change characteristic is linearly approximated within the displacement range of It is characterized by being. According to this structure, the range which correct | amends the change of the electromagnetic force with respect to a valve body displacement is limited in the range of the said valve body displacement from which the flow volume which passes the said small seat with respect to the largest displacement of a valve body changes. As a result, the elastic body having linear characteristics can be used to stabilize the valve body operation within the effective range of the electromagnetic control valve device and perform pressure control while maintaining a continuous pressure change. . In addition, small size and low cost can be realized.

  Further, in the electromagnetic control valve device, the elastic body is disposed so as to urge the valve body in a direction in which the valve body is pressed against the seat portion. In the case of the electromagnetic control valve device having this configuration, the effect of stabilizing the valve body operation described above is great, and stabilization of pressure control can be realized.

  In the electromagnetic control valve device, when the pressure difference (the fluid pressure difference before and after the fluid passes between the valve body and the seat portion) is ¼ or less of the maximum pressure applied to the electromagnetic control valve device (pressure Not only when there is no difference, but also when the current required for starting the valve body is a low-current required current when the pressure difference is sufficiently small with respect to the maximum pressure difference) The electromagnetic force relative to the displacement of the valve body when the required current during low pressure is applied to the electromagnetic force generation means within the range of displacement of the valve body where the flow rate passing between the valve body and the seat portion changes. It is characterized in that the elastic body has the load change rate of the same magnitude with the change rate with respect to the displacement when the change characteristic is approximated linearly and opposite in polarity.

  Further, the electromagnetic control valve device may be configured such that the flow path area formed between the valve body and the seat portion can be changed by movement of the valve body in a range smaller than a displacement range of the valve body. It is characterized in that the elastic body has a load change rate having the same magnitude as the rate of change of the electromagnetic force with respect to the displacement of the valve body when the operating current is applied to the electromagnetic force generating means. According to this configuration, as a range of the valve body displacement in which the flow rate passing between the valve body and the seat portion is changed by the valve body displacement, the valve body displacement of which the flow passage area is changed by the valve body displacement. By selecting the range, it is possible to select a range of displacement that is smaller than the maximum displacement of the valve body. Therefore, the electromagnetic force characteristics can be easily corrected by the load change rate of the elastic body having linear characteristics.

  The electromagnetic control valve device may further include an electromagnetic force characteristic correcting elastic body separately from the elastic body, and the total load change rate of the elastic body and the electromagnetic force characteristic correcting elastic body may be determined by moving the valve body. Electromagnetic force with respect to displacement of the valve body when the maximum operating current is applied to the electromagnetic force generating means within a range of displacement of the valve body in which a flow rate passing between the valve body and the seat portion changes. And the electromagnetic force characteristic correcting elastic body having the same rate of change and a load change rate of the same magnitude. According to this structure, the same effect can be acquired by adding the elastic body only for correction | amendment of an electromagnetic force characteristic.

  Further, as an automobile to which the present invention is applied, a brake caliper having a piston and a brake pad driven by hydraulic oil pressure, pressure generating means for generating the hydraulic oil pressure, and pressure for detecting the pressure of the pressure generating means A detecting means, a braking force control means for calculating a target braking force from a driver's operation and a vehicle state, and controlling a hydraulic oil pressure; between the pressure generating means and the brake caliper; and between a reservoir and the caliper. In the electronically controlled hydraulic brake device configured by the electromagnetic control valve device installed in the electromagnetic control valve device, the elastic body of the electromagnetic control valve device is configured to move the valve body and the seat portion by moving the valve body. The electromagnetic force with respect to the displacement of the valve body when the maximum operating current is applied to the electromagnetic force generation means within the range of displacement of the valve body in which the flow rate passing between them varies. The rate of change in polarity is configured to include an electronic control hydraulic brake apparatus comprises said elastic member having a load change rate of the same magnitude in the opposite. According to this configuration, in the hydraulic brake device in which the differential pressure of the fluid greatly changes before and after passing through the electromagnetic control valve device at a small flow rate, the valve body operation of the electromagnetic control valve device can be stabilized, It is possible to maintain a continuous pressure change when performing pressure control. Furthermore, at the same time, small size and low cost can be achieved. In addition, since the continuity of the pressure change is maintained, the pressure can be easily estimated and a feedforward operation can be performed, so that the responsiveness can be improved.

It is a figure which shows the cross-sectional schematic of the electromagnetic control valve apparatus used with the hydraulic brake device based on Example 1 of this invention. It is a figure showing the relationship between the electromagnetic force in the electromagnetic force generation means which concerns on the present Example 1, valve body displacement, and effective displacement. It is a figure showing the correction | amendment function of the electromagnetic force characteristic (refer the upper figure of FIG. 2) by the spring constant of the elastic body which concerns on the present Example 1. FIG. It is a figure showing the valve body displacement with respect to a ramp-shaped electric current input, and an inflow pressure change in the electromagnetic control valve apparatus of a prior art. It is a figure showing the relationship between the absolute value of the resultant force of the electromagnetic force and the elastic body load when the pressure difference is large and when the pressure difference is small, and the force by the passing fluid in the electromagnetic control valve device of the prior art. It is a figure showing the relationship between the absolute value of the resultant force of the electromagnetic force and elastic body load in the electromagnetic control valve apparatus which concerns on the present Example 1, and valve body displacement. It is a figure showing the relationship between the absolute value of the resultant force of the electromagnetic force, the elastic body load, and the force by the passing fluid when the pressure difference is large and when the pressure difference is small in the electromagnetic control valve device according to the first embodiment. It is a figure showing the inlet_port | entrance pressure change with respect to a ramp-shaped electric current input in the electromagnetic control valve apparatus which concerns on the present Example 1. FIG. It is a figure which shows another structure of the elastic body used for the electromagnetic control valve apparatus which concerns on the present Example 1. FIG. It is an electromagnetic control valve apparatus which concerns on Example 2 of this invention, Comprising: It is a whole block diagram of the electronically controlled hydraulic brake apparatus using the structure of Example 1. FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Electromagnetic force generation means 13 Cylinder 14 Valve body 15 Seat part 16 Elastic body 17 Driver circuit 18 Controller 19 Various sensors 20 Gap 202 Pump 203 Brake caliper 204 Reservoir 206 Hydraulic piping 207 Controller 208 Pressure sensor

Claims (7)

Current control means for calculating and outputting a current value corresponding to the target control amount, electromagnetic force generation means for changing the electromagnetic force generated by the applied current value, and movement by the electromagnetic force generated by the electromagnetic force generation means In an electromagnetic control valve device composed of a valve body that performs, a seat portion installed so as to face the valve body, and an elastic body that biases the valve body,
When there is no pressure difference between the fluid before and after passing between the valve body and the seat portion, when the current value necessary to separate the valve body from the seat portion is the maximum operating current, the valve When the maximum operating current is applied to the electromagnetic force generating means within the displacement range of the valve body in which the flow rate of the fluid passing between the valve body and the seat portion changes in conjunction with the movement of the body An electromagnetic control valve device comprising: the elastic body having a load change rate having the same magnitude as the rate of change of the electromagnetic force with respect to the displacement of the valve body but opposite in polarity. In claim 1,
The elastic body is a load having the same magnitude as the rate of change of the electromagnetic force with respect to the displacement of the valve body, but with the opposite polarity when the change characteristic of the electromagnetic force is linearly approximated within the range of displacement of the valve body. An electromagnetic control valve device characterized by being an elastic body having a linear characteristic with a change rate. In claim 1,
The electromagnetic control valve device, wherein the elastic body is disposed so as to urge the valve body in a direction in which the valve body is pressed against the seat portion. In claim 1,
When the pressure difference of the fluid before and after passing between the valve body and the seat portion is not equal to or less than the maximum pressure applied to the valve body instead of when there is no pressure difference, When the current required for starting is set as the current required at low pressure, within the range of displacement of the valve body in which the flow rate passing between the valve body and the seat portion changes in conjunction with the movement of the valve body, When the required current at the time of low pressure is applied to the electromagnetic force generating means, the rate of change with respect to displacement when the change characteristic of electromagnetic force with respect to the displacement of the valve body is approximated linearly and the load change with the same magnitude are opposite. An electromagnetic control valve device comprising: the elastic body having a linear characteristic having a rate. In claim 1,
The maximum operating current is set within the range that is smaller than the range of displacement of the valve body in which the flow rate of the fluid passing between the valve body and the seat portion changes in conjunction with the movement of the valve body. An electromagnetic control valve device, comprising: the elastic body having a load change rate of the same magnitude as the rate of change of the electromagnetic force with respect to the displacement of the valve body when the force is applied to the valve body. In claim 1,
An elastic body having a spring constant that prevents the valve body from being separated from the seat portion against the pressure applied to the valve body by the fluid when the current applied to the electromagnetic force generating means is zero is provided. Provide a correction elastic body for force characteristic correction,
The sum of the load change rates of the elastic body and the correcting elastic body is the same as the rate of change of the electromagnetic force with respect to the displacement of the valve body when the maximum operating current is applied to the electromagnetic force generating means. An electromagnetic control valve device characterized by its size. A brake caliper having a piston and a brake pad driven by the pressure of the hydraulic oil, a reservoir of the hydraulic fluid, a pressure generating means for generating the pressure of the hydraulic oil, and a pressure detecting means for detecting the pressure of the pressure generating means; A braking force control means for controlling a hydraulic oil pressure by calculating a target braking force from an operation amount by the driver and a driving state quantity of the vehicle; between the pressure generation means and the brake caliper; between the reservoir and the caliper; An automobile equipped with an electronically controlled hydraulic brake device comprising an electromagnetic control valve device installed in between,
When there is no pressure difference between the hydraulic oil before and after passing between the valve body that is moved by the electromagnetic force of the electromagnetic force generating means and is urged by the elastic body and the seat portion that is disposed opposite to the valve body, When the current value necessary for separating the valve body from the seat portion is the maximum operating current, the flow rate of the hydraulic oil passing between the valve body and the seat portion in conjunction with the movement of the valve body is When the maximum operating current is applied to the electromagnetic force generating means within the range of the displacement of the valve body that changes, the load change of the same magnitude with the rate of change of the electromagnetic force with respect to the displacement of the valve body is opposite to the positive and negative An automobile equipped with an electronically controlled hydraulic brake device having the electromagnetic control valve device, characterized by comprising the elastic body having a rate.