JP2010261509A - Hydraulic apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic apparatus capable of preventing a load applied to the drive of a sub-pump from increasing due to an increase in the hydraulic pressure of a portion on the upstream side of a regulator in a sub-passage in an engine high rotation. <P>SOLUTION: In the hydraulic apparatus, a first check valve 1118 closes according to an increase in a discharge capacity of a main pump 1102, and a supply passage of a working fluid discharged from the sub-pump 1103 is automatically changed according to the discharge capacity of the main pump 1102. The hydraulic device includes a bypass passage 1107 for connecting a portion on the upstream side of a primary regulator 1110 in the sub-passage 1105 and a portion on the downstream side of the primary regulator 1110 provided in the sub-passage 1105 while bypassing the primary regulator 1110, and a bypass regulator 1170 which is provided in the bypass passage 1107 to open according to the increase in the hydraulic pressure of the working fluid in the portion on the upstream side of the primary regulator 1110 in the sub-passage 1105. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a hydraulic apparatus, and more particularly, to a hydraulic apparatus that includes an engine-driven main pump and a sub pump, and switches a supply path of hydraulic oil discharged from the sub pump according to a discharge capacity of the main pump.

  In a hydraulic apparatus including an engine-driven oil pump that pumps hydraulic oil using the driving force of an internal combustion engine, the discharge capacity of the oil pump changes as the engine rotational speed changes. Therefore, at the time of engine low rotation where the discharge capacity of the oil pump becomes low, there is a possibility that the discharge capacity is insufficient and the required hydraulic pressure cannot be secured.

  On the other hand, in the hydraulic apparatus described in Patent Document 1, a sub pump is provided in addition to the main pump, and hydraulic oil is supplied from both the main pump and the sub pump to the hydraulic pressure demand section at the time of low engine speed. While ensuring the required oil pressure, the hydraulic oil discharged from the sub pump is recirculated to the oil pan as it is at the time of high engine speed. By adopting such a configuration, when the engine rotational speed increases, the discharge capacity of the main pump increases, and the hydraulic pressure required only by the hydraulic oil discharged from the main pump can be secured. The work of the sub pump is reduced. As a result, it is possible to suppress hydraulic pressure shortage at the time of low engine speed while suppressing the hydraulic oil from being wasted by the sub pump.

  As an example of the hydraulic device that switches the supply path of the hydraulic oil discharged from the sub pump as the discharge capacity of the main pump increases as described above, for example, a configuration including a regulator 5 and a check valve 8 as shown in FIG. Can be considered.

  As shown in FIG. 8, in this hydraulic apparatus, a main pump 1 and a sub pump 2 are provided as engine-driven oil pumps. A main passage 3 is connected to the main pump 1, and hydraulic oil pumped from the main pump 1 is supplied to the first hydraulic demand section and the second hydraulic demand section through the main passage 3. On the other hand, the sub pump 2 is connected to a sub passage 4 communicating with the second hydraulic demand section.

  A regulator 5 is provided in the main passage 3 and the sub passage 4. As shown in FIG. 8, the regulator 5 is provided on the downstream side of the portion (point P in FIG. 8) to which the first hydraulic pressure demand portion is connected in the main passage 3, and the spool valve is provided by the spring 5a. The main passage 3 and the sub passage 4 are always urged in the closing direction.

  As shown in FIG. 8, the regulator 5 is provided with a feedback passage 5 b that applies hydraulic pressure of hydraulic oil supplied to the first hydraulic pressure demand section to the spool valve. As a result, when the hydraulic pressure of the hydraulic oil supplied to the first hydraulic pressure demand section increases, a large hydraulic pressure acts on the spool valve accordingly, and the spool valve resists the urging force of the spring 5a. It is displaced to. The regulator 5 is provided with a main port 5c through which hydraulic oil flowing through the main passage 3 passes and a sub port 5d through which hydraulic oil flowing through the sub passage 4 passes. The shapes of the main port 5c and the sub port 5d are set so that the opening area changes as shown in FIG. 9 with respect to the amount of displacement of the spool valve toward the valve opening side.

  Specifically, as shown in FIG. 9, when the displacement amount of the spool valve toward the valve opening side is very small, both the main port 5 c and the sub port 5 d are closed, and the hydraulic oil in the main passage 3 and the sub passage 4 is blocked. Flow is inhibited by the regulator 5. When the hydraulic pressure acting on the spool valve increases through the feedback passage 5b and the amount of displacement of the spool valve toward the valve opening side increases, the opening area of the main port 5c first increases as shown by the solid line in FIG. The hydraulic oil flows downstream from the regulator 5 through the main passage 3. Then, when the hydraulic pressure acting on the spool valve through the feedback passage 5b further increases and the amount of displacement of the spool valve toward the valve opening side further increases, the opening area of the subport 5d begins to increase as shown by the broken line in FIG. In addition to the main passage 3, the hydraulic oil flows through the sub passage 4 downstream from the regulator 5. Here, as shown in FIG. 9, the larger the displacement amount of the spool valve toward the valve opening side, the larger the opening area of the main port 5 c and the sub port 5 d, and more than the regulator 5 through the main passage 3 and the sub passage 4. The amount of hydraulic oil supplied to the downstream side is increased. When the amount of displacement of the spool valve toward the valve opening side is equal to or greater than the predetermined amount X1, the opening area of the sub port 5d is larger than the opening area of the main port 5c, and the amount of hydraulic oil flowing through the main passage 3 through the main port 5c. The amount of hydraulic fluid flowing through the sub passage 4 through the sub port 5d is increased.

  The regulator 5 is connected to a linear solenoid 6 that outputs a control hydraulic pressure that biases the spool valve toward the valve closing side. As a result, the linear solenoid 6 is controlled to control the magnitude of the control hydraulic pressure that biases the spool valve toward the valve closing side, thereby opening the spool valve to the magnitude of the hydraulic pressure acting on the spool valve through the feedback passage 5b. The amount of hydraulic oil supplied to the first hydraulic pressure demand section can be controlled by changing the amount of displacement toward the valve.

  Further, as shown in FIG. 8, the main passage 3 and the sub passage 4 have a portion upstream of the portion (point P in FIG. 8) where the first hydraulic pressure demand portion is connected. A connecting passage 7 is provided that connects a portion upstream of the regulator 5. The connecting passage 7 is opened when the hydraulic oil pressure flowing through the portion on the sub passage 4 is larger than the hydraulic oil pressure flowing through the portion on the main passage 3 side in the connecting passage 7. A check valve 8 that allows only the flow of hydraulic oil from the passage 4 side to the main passage 3 side is provided.

  Immediately after the internal combustion engine is driven and hydraulic oil begins to be pumped from the main pump 1 and the sub pump 2, the engine rotation speed is low, so the hydraulic pressure supplied to the first hydraulic pressure demand section through the main passage 3 is very small. Therefore, at this time, the hydraulic pressure acting on the spool valve of the regulator 5 through the feedback passage 5b is very small, and both the main port 5c and the sub port 5d of the regulator 5 are closed. Therefore, the hydraulic oil discharged from the sub pump 2 is not supplied to the downstream side of the regulator 5, and the hydraulic pressure at the upstream side of the regulator 5 in the sub passage 4 gradually increases. The hydraulic pressure at the upstream side of the regulator 5 in the sub passage 4 is higher than the hydraulic pressure at the upstream side of the portion (point P in FIG. 8) of the main passage 3 to which the first hydraulic pressure demand portion is connected. When it becomes higher, the check valve 8 is opened, and the hydraulic oil discharged from the sub pump 2 flows into the main passage 3 through the connection passage 7. As a result, both the hydraulic oil discharged from the main pump 1 and the hydraulic oil discharged from the sub pump 2 are supplied to the first hydraulic pressure demand section through the main passage 3. Thus, both the hydraulic oil discharged from the main pump 1 and the hydraulic oil discharged from the sub pump 2 are supplied to the first hydraulic pressure demand section, and when the hydraulic pressure of the hydraulic oil supplied to the first hydraulic pressure demand section increases, the hydraulic oil is increased accordingly. Then, the hydraulic pressure acting on the spool valve of the regulator 5 increases through the feedback passage 5b, and the main port 5c is first opened. Then, both the hydraulic oil discharged from the main pump 1 and the hydraulic oil discharged from the sub pump 2 are supplied to the second hydraulic demand part through the main passage 3.

  Thus, in the above hydraulic apparatus, immediately after the internal combustion engine is driven and when the discharge capacity of the main pump 1 is low, the check valve 8 is opened and the hydraulic oil discharged from the main pump 1 And the hydraulic oil discharged from the sub pump 2 are supplied to each hydraulic pressure demand section through the main passage 3.

  On the other hand, when the engine speed increases and the discharge capacities of the main pump 1 and the sub pump 2 increase, the hydraulic pressure acting on the spool valve through the feedback passage 5b of the regulator 5 increases. The amount of displacement increases. When the displacement amount of the regulator 5 to the valve opening side of the spool valve increases in this way, the sub port 5d opens as shown in FIG. 9 so that the hydraulic oil is supplied to the downstream side of the regulator 5 in the sub passage 4. become. As a result, when the hydraulic pressure of the hydraulic fluid at the portion of the connecting passage 7 on the sub-passage 4 side decreases and the hydraulic pressure at this portion becomes lower than the hydraulic pressure of the hydraulic fluid at the side of the main passage 3 in the connecting passage 7, the check valve 8 is closed. I speak. Thus, when the discharge capacity of the main pump 1 is increased and the check valve 8 is closed, the hydraulic oil discharged from the sub pump 2 is not supplied to the first hydraulic demand part but supplied to the second hydraulic demand part through the sub passage 4. Will come to be.

  As described above, according to the hydraulic apparatus including the regulator 5 and the check valve 8, when the hydraulic pressure of the hydraulic oil discharged from the main pump 1 increases, the supply path of the hydraulic oil discharged from the sub pump 2 is automatically set. It will be switched. That is, according to such a configuration, the supply path of the hydraulic oil discharged from the sub pump 2 can be automatically switched without providing a sensor or the like for monitoring the hydraulic pressure of the hydraulic oil discharged from the main pump 1. Thus, when the hydraulic pressure required in the first hydraulic pressure demand section can be ensured only by the hydraulic oil discharged from the main pump 1, the work amount of the sub pump 2 can be reduced. Become.

JP 2003-193819 A

  By the way, generally, there is a limit to the amount of displacement of the regulator toward the valve opening side of the spool valve. In the regulator 5, as shown in FIG. 9, when the displacement amount reaches the maximum displacement amount Xmax, The opening area reaches the maximum value Smax and does not increase any more. Therefore, when the check valve 8 is closed as in the case of high engine speed and the displacement amount of the spool valve of the regulator 5 reaches the maximum displacement amount Xmax, the operation through the sub passage 4 is performed. The oil flow is limited by the magnitude of Smax, which is the maximum value of the opening area of the subport 5d. That is, as the engine rotational speed increases, the discharge capacity of the sub pump 2 increases, and when a large amount of hydraulic oil is discharged from the sub pump 2, the sub port 5d acts as a throttle, and the sub passage 4 The hydraulic pressure at the upstream side of the regulator 5 increases, and the load applied to drive the sub-pump 2 increases. As a result, in order to reduce the work amount of the sub-pump 2, the check valve 8 is closed and the hydraulic oil supply path is switched, but the effect may not be sufficiently obtained.

  Depending on the design specifications of the regulator 5, even when the opening area of the sub-port 5d is not maximized, the load of the sub-pump 2 may increase due to the small opening area of the sub-port 5d.

  Thus, in order to avoid that the effect of reducing the work amount of the sub-pump 2 due to the small opening area of the sub-port 5d is restricted, the opening area of the sub-port 5d with respect to the displacement amount of the spool valve is made larger. It is also conceivable to change the design of the regulator 5. However, when the design of the regulator 5 is changed so as to increase the opening area of the sub port 5d, the flow rate of the hydraulic oil flowing through the sub passage 4 rapidly changes with the displacement of the spool valve. There is a possibility that the spool valve vibrates or the check valve 8 vibrates with the rapid change of the.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to suppress an increase in the hydraulic pressure at a portion upstream of the regulator in the sub passage at the time of high engine rotation and an increase in the load on driving the sub pump. An object of the present invention is to provide a hydraulic device that can perform the above-described operation.

In the following, means for achieving the above object and its effects are described.
The invention according to claim 1 is an engine-driven main pump and sub pump, a main passage for supplying hydraulic oil discharged from the main pump to a hydraulic pressure demand section, a sub passage connected to the sub pump, A regulator that opens as the hydraulic oil pressure supplied to the hydraulic pressure demand section through the main passage increases and adjusts the hydraulic oil pressure in the main passage and the hydraulic oil in the sub passage; and the main passage And a connecting valve that connects the sub-passage to each other at a site upstream of the regulator, and a check valve that is provided in the connecting passage and allows only the flow of hydraulic oil from the sub-passage side to the main passage side The check valve closes as the discharge capacity of the main pump increases, and the supply path of hydraulic oil discharged from the sub pump is connected to the main pump. In the hydraulic apparatus that automatically switches according to the discharge capacity of the pump, the part bypassing the regulator is connected to the part upstream of the regulator in the sub-passage and the part downstream of the regulator in the sub-passage The gist is to include a bypass passage and an on-off valve that is provided in the bypass passage and opens as the hydraulic pressure of the hydraulic oil in a portion upstream of the regulator in the sub-passage increases.

  According to the above configuration, when the engine rotational speed increases, the discharge capacity of the main pump and the sub pump increases, and the hydraulic pressure at the upstream side of the regulator in the sub passage increases, the opening and closing provided in the bypass passage accordingly. The valve opens. Therefore, when the hydraulic pressure at the upstream side of the regulator in the sub passage increases, part of the hydraulic fluid in the sub passage flows around the regulator through the bypass passage. Accordingly, it is possible to suppress an increase in the hydraulic pressure at a portion upstream of the regulator in the sub passage at the time of high engine rotation and an increase in the load applied to driving the sub pump.

  In addition, in this way, the check valve provided in the connection passage is closed to reduce the work amount of the sub-pump, and the effect cannot be sufficiently obtained even though the hydraulic oil supply route is switched. Therefore, it is possible to suppress the deterioration of fuel consumption required for driving the sub pump.

  The invention according to claim 2 is the check valve according to claim 1, wherein the on-off valve includes a valve body and a biasing member that biases the valve body in a valve closing direction, When the check valve provided in the connection passage is closed, the hydraulic oil pressure in the upstream portion of the bypass passage in the bypass passage is greater than the hydraulic oil pressure in the downstream portion of the open / close valve. The gist is to open the valve when it becomes higher.

  According to a third aspect of the present invention, in the hydraulic apparatus according to the first aspect, the opening / closing valve includes a valve body and a biasing member that biases the valve body in a valve closing direction, and the opening / closing of the bypass passage. And a feedback passage that causes the hydraulic pressure of the hydraulic oil upstream of the valve to act on the valve body, and the hydraulic pressure of the hydraulic fluid upstream of the same opening / closing valve in the bypass passage increases. The main point is to open the valve.

  As the opening / closing valve for opening and closing the bypass passage, as described in claim 2, the hydraulic oil of the portion upstream of the opening / closing valve in the bypass passage has a hydraulic pressure downstream of the opening / closing valve. A check valve that opens when the hydraulic pressure of the hydraulic fluid becomes higher, or a regulator that opens as the hydraulic pressure of the hydraulic oil in a portion upstream of the opening / closing valve in the bypass passage increases as described in claim 3. Can be adopted.

  When a regulator is used as an on-off valve, the regulator opens when the check valve provided in the connection passage is closed, and the urging member or feedback so that hydraulic oil flows through the bypass passage. It is desirable to design the path configuration.

  According to a fourth aspect of the present invention, in the hydraulic device according to the first aspect, the on-off valve is a switching valve that is switched between a valve open state and a valve closed state by a control hydraulic pressure output from a solenoid. The apparatus includes an open / close state estimation means for estimating an open / close state of a check valve provided in the connection passage, and the open / close state estimation means estimates that the check valve provided in the connection passage is closed. The gist of the invention is to open the on-off valve by controlling the solenoid during operation.

  Further, as described above, when the estimation means for estimating the open / close state of the check valve provided in the connection passage is provided, and the check valve is estimated to be closed as the open / close valve for opening / closing the bypass passage, It is also possible to adopt a configuration that employs a switching valve that is switched to a valve open state by a control hydraulic pressure output from a solenoid.

  According to a fifth aspect of the present invention, in the hydraulic device according to the fourth aspect, the open / close state estimating means is based on the hydraulic pressure of the hydraulic oil and the engine rotational speed at a portion of the main passage to which the connection passage is connected. The gist is to estimate the open / closed state of the check valve provided in the connecting passage.

  The invention according to claim 6 is the hydraulic apparatus according to claim 5, wherein the open / close state estimation means is configured such that the hydraulic oil pressure of the portion of the main passage to which the connection passage is connected and the connection passage Corresponding to the current hydraulic pressure of the hydraulic fluid at the portion of the main passage to which the connecting passage is connected with reference to a calculation map showing a relationship with the minimum value of the engine rotational speed at which the check valve provided in the valve is closed The check valve provided in the connection passage is calculated based on the fact that the lowest engine value is calculated by comparing the lowest engine value with the current engine speed, and the current engine speed is equal to or higher than the lowest value. The gist is to estimate that the valve is closed.

  The check valve provided in the connection passage is closed when the hydraulic pressure of the hydraulic fluid on the main passage side is higher than the hydraulic pressure of the hydraulic fluid on the sub-passage side than the check valve in the connection passage. . Further, the higher the engine speed, the higher the discharge capacity of the main pump and the sub pump, and the oil pressure on the main passage side and the oil pressure on the sub passage side change according to the engine speed. Therefore, as a specific configuration of the open / close state estimation means for estimating the open / close state of the open / close valve provided in the connection passage, a portion where the connection passage in the main passage is connected as described in claim 5 above A configuration for estimating the open / close state of the check valve based on the hydraulic pressure of the hydraulic oil and the engine rotational speed can be employed.

  As a specific mode for estimating the open / closed state based on the hydraulic pressure in the main passage and the engine rotational speed, the operation of the portion of the main passage to which the connecting passage is connected as described in claim 6 above. A calculation map showing a relationship between the oil pressure of the oil and the minimum value of the engine rotation speed at which the check valve provided in the connection passage is closed is prepared in advance, and a configuration for estimating the open / close state with reference to this calculation map is adopted. be able to. In such a configuration, as described in claim 6, the minimum value corresponding to the current hydraulic pressure is calculated, and the calculated value is compared with the current engine speed. Then, it is estimated that the check valve provided in the connection passage is closed based on the current engine speed being equal to or higher than the lowest value.

  According to a seventh aspect of the present invention, in the hydraulic apparatus according to the fourth aspect, the open / close state estimation means includes a check valve provided in the connection passage based on the engine rotational speed being equal to or higher than a reference rotational speed. The gist is to estimate that the valve is closed.

  When the engine rotational speed is equal to or higher than the reference rotational speed by determining whether or not the discharge capacity of the main pump and the sub pump is increased based on whether the engine rotational speed is equal to or higher than the reference rotational speed as in the above configuration. In addition, based on this, it is possible to adopt a configuration for estimating that the check valve provided in the connection passage is closed. In order to accurately estimate that the check valve provided in the connection passage is closed based on the engine rotational speed being equal to or higher than the reference rotational speed, the reference rotational speed value is determined in advance by experiments, etc. It is desirable to set a value larger than the minimum value of the engine speed at which it is estimated that the check valve provided in the connection passage is surely closed based on the result.

  According to an eighth aspect of the present invention, the on / off switching valve is further provided at a portion downstream of the portion of the sub-passage to which the connection passage is connected and upstream of the portion of the bypass passage. The open / close switching valve is provided with a shut-off state in which the supply of hydraulic oil to a portion downstream of the open / close switching valve in the sub passage is shut off, and a portion downstream of the open / close switching valve in the sub passage. It is a hydraulic device as described in any one of Claims 1-7 switched to the communication state which accept | permits the supply of the hydraulic oil to.

  According to the above configuration, when the open / close switching valve is in the communication state, the check valve opens and closes according to the discharge capacity of the main pump, and the supply path of the hydraulic oil discharged from the sub pump is automatically switched. On the other hand, when the on / off switching valve is in the shut-off state, the hydraulic pressure in the portion upstream of the on / off switching valve in the sub passage increases, the check valve opens, and the hydraulic oil discharged from the sub pump It flows through the main passage together with the hydraulic oil discharged from the main pump. That is, by setting the open / close switching valve to the shut-off state, the hydraulic pressure on the side of the sub passage in the connecting passage is raised to open the check valve so that the hydraulic oil discharged from the sub pump can be introduced into the main passage. Become. That is, according to the above configuration, the hydraulic oil discharged from the sub pump can be quickly introduced into the main passage by switching the open / close switching valve to the shut-off state when the hydraulic pressure required in the hydraulic demand section increases. As a result, the hydraulic pressure of the hydraulic oil supplied to the hydraulic pressure demand section can be quickly increased.

  According to a ninth aspect of the present invention, in the hydraulic apparatus according to any one of the first to eighth aspects, the on-off valve has a maximum displacement amount to the valve opening side of the regulator, and the sub valve The gist is that the valve is opened when the opening area of the subport through which the hydraulic oil flowing through the passage passes is maximized.

  When the amount of displacement to the valve opening side of the regulator is maximized and the opening area of the subport in the regulator is maximized, the opening area of the subport does not increase further when the discharge capacity of the subpump increases. . Therefore, in this case, when the discharge capacity of the sub-pump increases, the sub-port acts as a throttle, and the flow rate of the hydraulic oil flowing through the sub-path tends to be limited. Therefore, as described in claim 9, when the amount of displacement of the regulator toward the valve opening side is at a maximum and the opening area of the subport is at a maximum, the on-off valve is opened. It is desirable to make it.

The schematic diagram which shows the structure of the continuously variable transmission provided with the hydraulic apparatus concerning 1st Embodiment of this invention. The schematic diagram which shows the structure of the hydraulic device concerning the embodiment. The graph which shows the relationship between the displacement amount of a spool valve, and the opening area of a main port and a subport. The schematic diagram which shows the structure of the hydraulic device concerning the example of a change of the embodiment. The schematic diagram which shows the structure of the hydraulic device concerning the example of a change of the embodiment. The graph which shows the relationship between the oil_pressure | hydraulic supplied to the hydraulic circuit for transmission, and the minimum value of the engine speed which a 1st check valve closes. The schematic diagram which shows the structure of the hydraulic device concerning 2nd Embodiment of this invention. The schematic diagram which shows the structure of the conventional hydraulic device. The graph which shows the relationship between the displacement amount of the spool valve in the conventional hydraulic device, and the opening area of a main port and a subport.

(First embodiment)
A first embodiment in which the hydraulic device according to the present invention is embodied as a hydraulic device for a continuously variable transmission mounted on an automobile will be described below with reference to FIGS. FIG. 1 shows a schematic configuration of a continuously variable transmission including a hydraulic device according to the present embodiment.

  As shown in FIG. 1, the continuously variable transmission 10 according to this embodiment includes a torque converter 11 and a forward / reverse switching mechanism 19. The input shaft 12 of the torque converter 11 is connected to an output shaft of an internal combustion engine (not shown). The torque converter 11 includes a lockup clutch 13.

  The output shaft of the torque converter 11 is connected to the input shaft of the forward / backward switching mechanism 19. As shown in FIG. 1, the forward / reverse switching mechanism 19 includes a forward clutch C1 and a reverse brake B1, and is input by selectively engaging either the forward clutch C1 or the reverse brake B1. Switching between a forward state in which the rotational force is output as it is and a reverse state in which the rotational force is reversed and output as a reverse rotational force.

  The output shaft 14 of the forward / backward switching mechanism 19 is connected to the primary pulley 15 of the continuously variable transmission 10. As shown in FIG. 1, a metal belt 17 is wound around the primary pulley 15 and the secondary pulley 16 of the continuously variable transmission 10. And the output shaft 18 connected with the secondary pulley 16 is connected to the drive wheel via the reduction gear and differential which are not shown in figure.

  Thereby, in the continuously variable transmission 10 of the present embodiment, the driving force of the internal combustion engine is transmitted to the primary pulley 15 via the torque converter 11 and the forward / reverse switching mechanism 19. The driving force transmitted from the primary pulley 15 to the secondary pulley 16 via the belt 17 is transmitted to the driving wheels via the reduction gear and the differential.

  Inside the primary pulley 15 and the secondary pulley 16 are formed hydraulic chambers (not shown), and the hydraulic pressure in the hydraulic chambers is changed by the hydraulic device 100. When the oil pressure in the hydraulic chambers of the pulleys 15 and 16 is changed in this way, the groove width of the pulleys 15 and 16 is changed, and the winding radius of the belt 17 wound around the pulleys 15 and 16 is changed. . Thus, the gear ratio in the continuously variable transmission 10 is changed by changing the winding radius of the belt 17.

  As shown in FIG. 1, the hydraulic device 100 controls the amount of hydraulic oil supplied to the hydraulic chambers of the pulleys 15 and 16 to change the gear ratio, and forward clutch C1 of the forward / reverse switching mechanism 19. And a shift hydraulic circuit 120 for operating the forward / reverse switching mechanism 19 by controlling the amount of hydraulic oil supplied to the piston of the reverse brake B1. Further, the hydraulic oil is supplied to the torque converter 11 and the hydraulic oil for the torque converter 130 for controlling the amount of hydraulic oil supplied to the lockup clutch 13 and the hydraulic oil is supplied to each part of the continuously variable transmission 10 as lubricating oil. And a hydraulic pressure supply circuit 110 that supplies hydraulic oil to each of the hydraulic circuits 120, 130, and 140.

  The hydraulic device 100 is controlled by the electronic control device 20. The electronic control unit 20 includes a CPU that executes arithmetic processing related to various controls, a ROM that stores programs and data necessary for the control, a RAM that temporarily stores arithmetic results of the CPU, and the like. .

  Connected to the electronic control unit 20 are an accelerator position sensor 21 for detecting the accelerator pedal operation amount ACCP by the driver, a vehicle speed sensor 22 for detecting the vehicle speed SPD, a rotational speed sensor 23 for detecting the engine rotational speed NE, and the like. The output signals from these various sensors are captured. The electronic control unit 20 performs various calculations based on output signals taken from these various sensors, and controls the hydraulic device 100 to control the lockup clutch 13, the gear ratio, and the forward / reverse switching mechanism 19 of the continuously variable transmission 10. Output control commands.

  Hereinafter, the configuration of the hydraulic device 100, particularly the configuration of the hydraulic pressure supply circuit 110, will be described in detail with reference to FIG. FIG. 2 is a schematic diagram showing a schematic configuration of the hydraulic apparatus 100 according to the present embodiment.

  As shown in FIG. 2, the hydraulic pressure supply circuit 110 includes an engine-driven main pump 1102 and a sub-pump 1103 that are driven by the driving force of the internal combustion engine and pump hydraulic fluid stored in the oil pan 1101.

  A main passage 1104 is connected to the main pump 1102, and hydraulic oil pressure-fed from the main pump 1102 passes through the main passage 1104, as shown in FIG. Is supplied to the hydraulic circuit 130 for lubrication and the hydraulic circuit 140 for lubrication. On the other hand, a sub-passage 1105 communicating with the lubricating hydraulic circuit 140 is connected to the sub-pump 1103.

As shown in FIG. 2, a primary regulator 1110 and a secondary regulator 1120 are provided in the main passage 1104 and the sub passage 1105.
The primary regulator 1110 is downstream of the portion of the main passage 1104 where the speed change hydraulic circuit 120 is connected (point P in FIG. 2) and the portion where the torque converter hydraulic circuit 130 is connected (point Q in FIG. 2). ) Above the upstream side. The spool valve is always urged by the spring 1111 in the direction of closing the main passage 1104 and the sub passage 1105. The primary regulator 1110 is provided with a feedback passage 1112 that applies hydraulic pressure of the hydraulic oil supplied to the shift hydraulic circuit 120 to the spool valve. As a result, as the hydraulic pressure of the hydraulic fluid supplied to the gear shift hydraulic circuit 120 increases, a larger hydraulic pressure acts on the spool valve through the feedback passage 1112, and the spool valve moves toward the valve opening side against the urging force of the spring 1111. It will be displaced.

  The primary regulator 1110 is provided with a main port 1113 through which hydraulic oil flowing through the main passage 1104 passes and a subport 1114 through which hydraulic oil flowing through the sub passage 1105 passes. The shapes of the main port 1113 and the sub port 1114 are set so that the opening area with respect to the amount of displacement of the spool valve toward the valve opening side changes as shown in FIG. Specifically, when the displacement amount to the valve opening side is very small, both the main port 1113 and the sub port 1114 are closed, and the flow of hydraulic oil in the main passage 1104 and the sub passage 1105 is prohibited by the primary regulator 1110. Then, when the hydraulic pressure acting on the spool valve through the feedback passage 1112 increases and the amount of displacement of the spool valve toward the valve opening increases, first, the opening area of the main port 1113 increases as shown by the solid line in FIG. The hydraulic oil flows downstream from the primary regulator 1110 through the main passage 1104. Then, the hydraulic pressure acting on the spool valve through the feedback passage 1112 further increases, and when the displacement amount of the spool valve further increases, the opening area of the subport 1114 begins to increase, and from the primary regulator 1110 through the sub passage 1105 in addition to the main passage 1104. Also, the hydraulic oil flows downstream.

  Here, as shown in FIG. 3, the larger the displacement amount of the spool valve toward the valve opening side, the larger the opening area of the main port 1113 and the sub port 1114, and from the primary regulator 1110 through the main passage 1104 and the sub passage 1105. Also, the amount of hydraulic oil supplied downstream is increased. At this time, when the displacement amount is equal to or larger than the predetermined amount X1, the opening area of the sub port 1114 is larger than the opening area of the main port 1113, and the sub port 1114 has a smaller amount of hydraulic oil flowing through the main passage 1104 through the main port 1113. The amount of hydraulic oil flowing through the passage 1105 is increased.

  As shown in FIG. 2, the secondary regulator 1120 is downstream of the portion (point Q in FIG. 2) where the torque converter hydraulic circuit 130 is connected in the main passage 1104 and is connected to the lubricating hydraulic circuit 140. It is provided at a site upstream of the site (point R in FIG. 2). The spool valve is always urged by the spring 1121 in a direction to close the main passage 1104 and the sub passage 1105. The secondary regulator 1120 is provided with a feedback passage 1122 that applies hydraulic pressure of hydraulic oil supplied to the torque converter hydraulic circuit 130 to the spool valve. As a result, as the hydraulic pressure of the hydraulic fluid supplied to the torque converter hydraulic circuit 130 increases, a larger hydraulic pressure acts on the spool valve through the feedback passage 1122, and the spool valve resists the biasing force of the spring 1121. Will be displaced.

  Similarly to the primary regulator 1110, the secondary regulator 1120 is also provided with a main port 1123 through which the hydraulic oil flowing through the main passage 1104 passes and a subport 1124 through which the hydraulic oil flowing through the sub passage 1105 passes. The shapes of the main port 1123 and the sub port 1124 are set so that the opening area with respect to the displacement amount of the spool valve toward the valve opening side changes as shown in FIG. Yes.

  The primary regulator 1110 and the secondary regulator 1120 are connected to linear solenoids 1115 and 1125, respectively, that output control oil pressure that biases the spool valve in the valve closing direction. Thus, by controlling the linear solenoids 1115 and 1125 and changing the magnitude of the control hydraulic pressure, the displacement amount of the spool valve with respect to the magnitude of the hydraulic pressure acting through the feedback passages 1112 and 1122 is changed, and the shift hydraulic pressure The hydraulic pressure of hydraulic fluid supplied to the circuit 120 and the torque converter hydraulic circuit 130 can be controlled. Note that the control of the control hydraulic pressure output from the linear solenoids 1115 and 1125 is performed by the electronic control unit 20.

  As shown in FIG. 2, the main passage 1104 and the sub passage 1105 merge at a portion downstream from the secondary regulator 1120 (point R in FIG. 2), and through the main passage 1104 and the sub passage 1105, than the secondary regulator 1120. The hydraulic fluid flowing downstream is supplied to the lubricating hydraulic circuit 140.

  Further, a lubrication regulator 1130 including a drain port 1133 is connected to a portion where the main passage 1104 and the sub passage 1105 merge (point R in FIG. 2). In the lubrication regulator 1130, the spool valve is always urged in the valve closing direction by the spring 1131. The lubrication regulator 1130 is provided with a feedback passage 1132 that applies hydraulic pressure of hydraulic oil supplied to the lubrication hydraulic circuit 140 to the spool valve. As a result, as the hydraulic pressure of the hydraulic fluid supplied to the lubricating hydraulic circuit 140 increases, a larger hydraulic pressure acts on the spool valve through the feedback passage 1132, and the spool valve moves toward the valve opening side against the urging force of the spring 1131. Displacement increases the opening area of the drain port 1133. As shown in FIG. 2, the drain port 1133 of the lubrication regulator 1130 is connected to a drain passage 1106 for returning the working oil to the upstream side of the main pump 1102 and the sub pump 1103. Thus, the spool valve is displaced to the valve opening side. As a result, the hydraulic oil is recirculated through the drain passage 1106.

  As shown in FIG. 2, the main regulator 1104 and the primary regulator in the sub-passage 1105 are located upstream of the part (point P in FIG. 2) connected to the transmission hydraulic circuit 120 in the main passage 1104. A first connection passage 1117 is provided for communicating with a portion upstream of 1110. The first connecting passage 1117 is opened when the hydraulic pressure of the hydraulic fluid flowing through the portion on the sub passage 1105 is larger than the hydraulic pressure of the hydraulic fluid flowing through the portion on the main passage 1104 side in the first connecting passage 1117. Thus, a first check valve 1118 that allows only the flow of hydraulic oil from the sub passage 1105 side to the main passage 1104 side is provided.

  Further, the main passage 1104 is located downstream of the primary regulator 1110 and upstream of the portion to which the torque converter hydraulic circuit 130 is connected (point Q in FIG. 2). A second connection passage 1127 is provided in the passage 1105, which is downstream from the primary regulator 1110 and communicates with a portion upstream from the secondary regulator 1120. The second connection passage 1127 is opened when the hydraulic pressure of the hydraulic fluid flowing through the portion on the sub passage 1105 is larger than the hydraulic pressure of the hydraulic fluid flowing through the portion on the main passage 1104 side in the second connection passage 1127. A second check valve 1128 that allows only the flow of hydraulic oil from the sub passage 1105 side to the main passage 1104 side is provided.

  Immediately after the internal combustion engine is driven and hydraulic oil begins to be pumped from the main pump 1102 and the sub pump 1103, the hydraulic pressure supplied to the shifting hydraulic circuit 120 through the main passage 1104 is very small. Therefore, the hydraulic pressure acting on the spool valve of the primary regulator 1110 through the feedback passage 1112 is very small. Therefore, in the hydraulic apparatus 100 of the present embodiment, at this time, both the main port 1113 and the sub port 1114 of the primary regulator 1110 are closed. Therefore, the hydraulic oil discharged from the sub pump 1103 is not supplied to the downstream side of the primary regulator 1110, and the hydraulic pressure at the upstream side of the primary regulator 1110 in the sub passage 1105 gradually increases.

  Thus, the hydraulic pressure at the upstream side of the primary regulator 1110 in the sub passage 1105 is higher than the hydraulic pressure at the upstream side of the portion (point P in FIG. 2) of the main passage 1104 to which the speed change hydraulic circuit 120 is connected. Then, the first check valve 1118 is opened, and the hydraulic oil discharged from the sub pump 1103 through the first connection passage 1117 flows into the main passage 1104. Then, both the hydraulic oil discharged from the main pump 1102 and the hydraulic oil discharged from the sub pump are supplied to the transmission hydraulic circuit 120 through the main passage 1104.

  Thus, when both the hydraulic oil discharged from the main pump 1102 and the hydraulic oil discharged from the sub pump 1103 are supplied to the transmission hydraulic circuit 120 and the hydraulic pressure of the hydraulic oil supplied to the transmission hydraulic circuit 120 increases, As a result, the hydraulic pressure acting on the spool valve of the primary regulator 1110 increases through the feedback passage 1112. As a result, first, the main port 1113 is opened.

  By opening the main port 1113 in this manner, the hydraulic oil is supplied to a portion of the main passage 1104 downstream of the primary regulator 1110, and the hydraulic oil discharged from the main pump 1102 and the sub-pump 1103 are discharged. Both hydraulic oil and hydraulic oil are supplied to the torque converter hydraulic circuit 130 through the main passage 1104.

  Then, the hydraulic pressure of the hydraulic oil supplied to the torque converter hydraulic circuit 130 through the main passage 1104 acts on the spool valve of the secondary regulator 1120 through the feedback passage 1122, and the main port 1123 opens. By opening the main port 1123 in this way, the hydraulic oil is supplied to a portion of the main passage 1104 downstream of the secondary regulator 1120, and the hydraulic oil discharged from the main pump 1102 and the sub-pump 1103 are discharged. Both the hydraulic oil and the hydraulic oil are supplied to the lubricating hydraulic circuit 140 through the main passage 1104.

  Thus, immediately after the internal combustion engine is driven and hydraulic oil starts to be pumped from the main pump 1102 and the sub pump 1103, and when the discharge capacity of the main pump 1102 is low, the check valve 1118 opens. Then, both the hydraulic oil discharged from the main pump 1102 and the hydraulic oil discharged from the sub pump 1103 are supplied to the hydraulic circuits 120, 130, and 140 through the main passage 1104.

  On the other hand, when the engine speed NE increases and the discharge capacities of the main pump 1102 and the sub pump 1103 increase, the hydraulic pressure acting on the spool valve through the feedback passage 1112 of the primary regulator 1110 increases. The amount of displacement increases.

  When the displacement amount of the primary regulator 1110 to the valve opening side of the spool valve increases in this way, the sub port 1114 opens as shown in FIG. 3, and hydraulic oil is supplied to the downstream side of the primary regulator 1110 through the sub passage 1105. Become so. When hydraulic oil is supplied to the downstream side of the primary regulator 1110 through the sub passage 1105 in this way, the hydraulic pressure of the hydraulic oil at the portion on the sub passage 1105 side in the first connection passage 1117 decreases.

  When the discharge capacities of the main pump 1102 and the sub pump 1103 further increase with the increase in the engine speed NE, the hydraulic pressure of the hydraulic oil in the portion on the sub passage 1105 side in the first connection passage 1117 is changed in the first connection passage 1117. The first check valve 1118 closes because the hydraulic pressure is lower than the hydraulic oil pressure on the main passage 1104 side.

  In the hydraulic apparatus 100 according to the present embodiment, the discharge capacity of the main pump 1102 can cover the hydraulic oil required in the transmission hydraulic circuit 120 only by the hydraulic oil discharged from the main pump 1102. The primary regulator 1110 is designed so that the first check valve 1118 is closed when the level becomes 1 level L1 or higher.

  Thus, when the discharge capacity of the main pump 1102 becomes equal to or higher than the first level L1 and the first check valve 1118 is closed, the hydraulic oil discharged from the sub pump 1103 is not supplied to the transmission hydraulic circuit 120, but the primary regulator 1110 It is supplied to the downstream side.

  Thus, when the hydraulic oil discharged from the sub pump 1103 is supplied to the downstream side of the primary regulator 1110 without being supplied to the transmission hydraulic circuit 120, the hydraulic oil at a site on the sub passage 1105 side in the second connection passage 1127. Becomes higher than the hydraulic pressure of the hydraulic oil at the site on the main passage 1104 side in the second connection passage 1127, and the second check valve 1128 is opened. As a result, the hydraulic oil discharged from the sub pump 1103 flows into the main passage 1104 through the second connection passage 1127 and is supplied to the torque converter hydraulic circuit 130 and the lubrication hydraulic circuit 140 through the main passage 1104.

At this time, the hydraulic oil discharged from the main pump 1102 is supplied to all of the hydraulic circuits 120, 130, and 140 through the main passage 1104.
By the way, when the first check valve 1118 is closed in this way and the engine rotational speed NE further increases and the discharge capacities of the main pump 1102 and the sub pump 1103 further increase, the spool valve passes through the feedback passage 1122 of the secondary regulator 1120. Since the hydraulic pressure acting on the valve increases, the amount of displacement of the spool valve increases.

  When the amount of displacement of the spool valve of the secondary regulator 1120 increases in this way, the sub port 1124 opens as shown in FIG. 3, and hydraulic oil is supplied to the downstream side of the secondary regulator 1120 through the sub passage 1105. When hydraulic oil is supplied to the downstream side of the secondary regulator 1120 through the sub passage 1105 in this way, the hydraulic pressure of the hydraulic oil at the portion on the sub passage 1105 side in the second connection passage 1127 decreases.

  When the discharge capacities of the main pump 1102 and the sub pump 1103 further increase with the increase in the engine speed NE, the hydraulic pressure of the hydraulic oil at the portion on the sub passage 1105 side in the second connection passage 1127 is changed in the second connection passage 1127. The second check valve 1128 closes because the hydraulic pressure is lower than the hydraulic oil pressure on the main passage 1104 side.

  In the hydraulic apparatus 100, the hydraulic fluid required for the transmission hydraulic circuit 120 and the torque converter hydraulic circuit 130 is discharged only by the hydraulic oil discharged from the main pump 1102 because the discharge capacity of the main pump 1102 is only. The secondary regulator 1120 is designed so that the second check valve 1128 closes when the second level L2 that can be covered is reached.

  Thus, when the discharge capacity of the main pump 1102 exceeds the second level L2 and the second check valve 1128 is closed, the hydraulic oil discharged from the sub pump 1103 is transferred to the transmission hydraulic circuit 120 and the torque converter hydraulic circuit 130. Instead of being supplied, it is supplied to the lubricating hydraulic circuit 140 on the downstream side of the secondary regulator 1120.

At this time, the hydraulic oil discharged from the main pump 1102 is supplied to all the hydraulic circuits 120, 130, and 140 through the main passage 1104.
Further, when the amount of hydraulic fluid supplied from the main passage 1104 and the sub passage 1105 to the lubricating hydraulic circuit 140 is larger than the amount of hydraulic fluid required in the lubricating hydraulic circuit 140, the lubricating regulator 1130 is passed through the feedback passage 1132. The hydraulic pressure acting on the spool valve increases, and the drain port 1133 opens. As a result, part of the hydraulic oil is recirculated through the drain passage 1106, and the hydraulic pressure of the hydraulic oil supplied to the lubricating hydraulic circuit 140 is suppressed from becoming excessively high.

  Thus, in the hydraulic apparatus 100 of the present embodiment, when the engine rotational speed NE is low and the discharge capacity of the main pump 1102 is less than the first level L1, the hydraulic oil discharged from the main pump 1102 and the sub pump 1103 Both the discharged hydraulic oil is supplied to all the hydraulic circuits 120, 130, and 140.

  On the other hand, when the discharge capacity of the main pump 1102 is equal to or higher than the first level L1 and lower than the second level L2, the hydraulic oil discharged from the sub pump 1103 is not supplied to the speed change hydraulic circuit 120 and is converted to the torque converter. Is supplied to the hydraulic circuit 130 for lubrication and the hydraulic circuit 140 for lubrication.

  When the discharge capacity of the main pump 1102 is equal to or higher than the second level L2, the hydraulic oil discharged from the sub pump 1103 is not supplied to the transmission hydraulic circuit 120 and the torque converter hydraulic circuit 130, and only the lubricating hydraulic circuit 140 is supplied. Will be supplied to.

  That is, the supply path of the hydraulic oil discharged from the sub pump 1103 is automatically switched according to the discharge capacity of the main pump 1102, and the work amount of the sub pump 1103 is reduced as the discharge capacity of the main pump 1102 increases. It has become.

  Incidentally, as shown in FIG. 3, there is a limit to the amount of displacement of the primary regulator 1110 toward the opening side of the spool valve. When the displacement amount reaches the maximum displacement amount Xmax, the opening area of the sub-port 1114 reaches the maximum value Smax and does not increase any more. Therefore, when the first check valve 1118 is closed and the displacement amount of the spool valve of the primary regulator 1110 reaches the maximum displacement amount Xmax as in the case of high engine speed, the sub-passage 1105 The flow of hydraulic fluid through the sub-port 1114 is limited by the magnitude of Smax, which is the maximum value of the opening area of the subport 1114.

  That is, as the engine rotational speed NE increases, the discharge capacity of the sub pump 1103 increases. When a large amount of hydraulic oil is discharged from the sub pump 1103, the sub port 1114 acts as a throttle, and the sub pump 1103 The load applied to driving increases.

  As a result, the load applied to drive the sub pump 1103 increases at a high engine speed, and the first check valve 1118 is closed to switch the hydraulic oil supply path in order to reduce the work amount of the sub pump 1103. Nevertheless, the effect may not be sufficiently obtained.

  Therefore, in the hydraulic apparatus 100 of the present embodiment, a bypass path 1107 that bypasses the primary regulator 1110 is further provided in the hydraulic pressure supply circuit 110 as shown in FIG.

  Specifically, as shown in FIG. 2, a portion of the sub passage 1105 that is downstream of the portion where the first connection passage 1117 is connected and upstream of the primary regulator 1110, and the primary regulator of the sub passage 1105 A bypass passage 1107 is provided that connects a portion downstream of 1110 and a portion upstream of the portion to which the second connecting passage 1127 is connected. A bypass regulator 1170 is provided in the middle of the bypass passage 1107 as shown in FIG. In the bypass regulator 1170, the spool valve is always urged toward the valve closing side by the spring 1171. The bypass regulator 1170 is provided with a feedback passage 1172 that causes the hydraulic pressure of the hydraulic oil in the sub-passage 1105 upstream of the primary regulator 1110 to act on the spool valve.

  As a result, in the hydraulic apparatus 100 according to the present embodiment, the hydraulic pressure increases as the hydraulic oil pressure upstream of the primary regulator 1110 in the sub-passage 1105 increases and acts on the spool valve through the feedback passage 1172. The valve is displaced to the valve opening side against the urging force of the spring 1171. As a result, a part of the hydraulic oil upstream of the primary regulator 1110 in the sub passage 1105 flows through the bypass passage 1107 to a portion downstream of the primary regulator 1110.

  In the bypass regulator 1170, when the displacement amount of the primary regulator 1110 to the valve opening side of the spool valve is the maximum displacement amount Xmax, and the opening area of the subport 1114 is maximum, the spool valve Is set so that the urging force of the spring 1171 and the passage step area of the feedback passage 1172 are displaced.

According to the first embodiment described above, the following operational effects can be obtained.
(1) When the engine rotational speed NE rises, the discharge capacities of the main pump 1102 and the sub pump 1103 increase, and the hydraulic pressure at the upstream side of the primary regulator 1110 in the sub passage 1105 increases, along with this, the bypass passage 1107 The spool valve of the provided bypass regulator 1170 is displaced to the valve opening side. Therefore, when the sub port 1114 acts as a throttle and the hydraulic pressure at the upstream side of the primary regulator 1110 in the sub passage 1105 increases, part of the hydraulic oil in the sub passage 1105 bypasses the primary regulator 1110 through the bypass passage 1107. Will begin to flow. Therefore, it is possible to suppress an increase in the load on the drive of the sub-pump 1103 due to an increase in the hydraulic pressure at a portion upstream of the primary regulator 1110 in the sub-passage 1105 during high engine speed. This also causes the inconvenience that the first check valve 1118 is closed to reduce the work amount of the sub-pump 1103 and the effect is not sufficiently obtained even though the hydraulic oil supply path is switched. Thus, it is possible to suitably suppress the deterioration of fuel consumption required to drive the sub pump 1103.

The first embodiment can also be implemented in the following forms that are appropriately modified.
In the above embodiment, when the displacement amount of the primary regulator 1110 to the valve opening side is the maximum displacement amount Xmax and the opening area of the subport 1114 is the maximum value Smax, the bypass regulator 1170 is opened. The configuration in which the biasing force of the spring 1171 and the cross-sectional area of the feedback passage 1172 are set so as to be valved is shown. On the other hand, depending on the design specifications of the primary regulator 1110, even when the opening area of the subport 1114 is not the maximum value Smax, the load of the subpump 1103 is reduced due to the small opening area of the subport 1114. It may increase. Therefore, it is desirable to change the configuration of the bypass regulator 1170 as appropriate according to the design specifications of the primary regulator 1110. That is, the spring 1171 is attached according to the design specifications of the primary regulator 1110 so that the bypass regulator 1170 is opened when there is a risk that the hydraulic pressure in the upstream side of the primary regulator 1110 in the sub passage 1105 may increase. What is necessary is just to set the cross-sectional area of the force and the feedback path 1172.

  -In the said 1st Embodiment, the structure which provided the bypass regulator 1170 as an on-off valve which opens and closes the bypass path 1107 was shown. On the other hand, as the on-off valve, a configuration in which a check valve including a valve body and an urging member such as a spring that urges the valve body in a valve closing direction can be employed. That is, instead of the bypass regulator 1170 in the first embodiment, a configuration in which a check valve such as a check ball or a check plate is provided may be employed. If such a configuration is adopted, the check valve is opened when the hydraulic pressure of the hydraulic oil in the upstream portion of the bypass passage 1107 is higher than the hydraulic pressure of the hydraulic fluid in the downstream portion of the check valve. To come. Therefore, as in the first embodiment, when the sub port 1114 acts as a throttle and the hydraulic pressure at the upstream side of the primary regulator 1110 in the sub passage 1105 increases, part of the hydraulic oil in the sub passage 1105 bypasses. It flows to bypass the primary regulator 1110 through the passage 1107. Therefore, even when such a configuration is adopted, the same operational effect as (1) described in the first embodiment can be obtained.

  In the above embodiment, the present invention is applied to the hydraulic device 100 including the hydraulic supply circuit 110 that switches the work amount of the sub-pump 1103 in three stages using the first check valve 1118 and the second check valve 1128. showed that. On the other hand, the present invention can also be applied to the hydraulic apparatus 100 including the hydraulic supply circuit 110 that switches the work amount of the sub-pump 1103 in four stages.

  Specifically, as shown in FIG. 4, the lubrication regulator 1130 is changed to one having a subport 1134, similar to the primary regulator 1110 and the secondary regulator 1120. Then, the sub passage 1105 on the downstream side of the secondary regulator 1120 is connected to the lubrication regulator 1130. Further, the main passage 1104 communicates with the portion of the main passage 1104 connected to the lubricating hydraulic circuit 140 to the portion of the sub passage 1105 that is downstream of the secondary regulator 1120 and upstream of the lubrication regulator 1130. A third connection passage 1137 is provided. Then, when the hydraulic pressure of the hydraulic fluid flowing through the portion on the sub-passage 1105 side is larger than the hydraulic pressure of the hydraulic fluid flowing through the portion on the main passage 1104 side in the third connection passage 1137, the third connection passage 1137 is opened. A third check valve 1138 that allows only the flow of hydraulic oil from the sub passage 1105 side to the main passage 1104 side is provided.

  According to such a configuration, the discharge capacity of the main pump 1102 further increases from the second level L2, and all the supply of hydraulic oil to the hydraulic circuits 120, 130, 140 is performed only by the hydraulic oil discharged from the main pump 1102. When the third level L3 or higher that can be covered is reached, the third check valve 1138 is closed and the hydraulic oil discharged from the sub-pump 1103 is not supplied to any of the hydraulic circuits 120, 130, 140, and the drain passage. Reflux through 1106. Thereby, the work amount of the sub pump 1103 can be further reduced, and the fuel consumption of the internal combustion engine due to the driving load of the sub pump 1103 can be further suppressed.

  Even in the hydraulic device that switches the work amount of the sub-pump 1103 in four stages as described above, the bypass passage 1107 and the bypass regulator 1170 are provided as shown in FIG. It becomes possible to obtain the same operational effects.

In the first embodiment, the configuration in which the bypass regulator 1170 is provided as an on-off valve that opens and closes the bypass passage 1107 is illustrated. However, the control that is output from the solenoid as the on-off valve that opens and closes the bypass passage 1107. It is also possible to adopt a configuration in which a switching valve whose opening and closing state is switched by hydraulic pressure is provided.
Specifically, as shown in FIG. 5, instead of the bypass regulator 1170, a bypass switching valve 1180 in which the spool valve is always urged in the valve closing direction by a spring 1181 is provided in the middle of the bypass passage 1107. The bypass switching valve 1180 is connected to a solenoid 1185 that applies a control hydraulic pressure to the spool valve based on a control command from the electronic control unit 20.

  According to such a configuration, the spool valve of the bypass switching valve 1180 is displaced toward the valve opening side against the urging force of the spring 1181 by outputting the control hydraulic pressure from the solenoid 1185 based on the control command from the electronic control unit 20. Then, the hydraulic oil in the sub passage 1105 flows downstream from the primary regulator 1110 through the bypass passage 1107.

  In the case of adopting such a configuration, it is estimated that the electronic control unit 20 functions as an open / close state estimating means for estimating the open / close state of the first check valve 1118 and the first check valve 1118 is closed. The bypass switching valve 1180 is opened.

  The first check valve 1118 provided in the first connection passage 1117 is such that the hydraulic oil pressure on the main passage 1104 side of the first connection passage 1117 is closer to the sub-passage than the first check valve 1118. The valve is closed when the hydraulic pressure of the hydraulic oil on the 1105 side becomes higher. Further, as the engine rotational speed NE is higher, the discharge capacities of the main pump 1102 and the sub pump 1103 are higher, and the hydraulic pressure on the main passage 1104 side and the hydraulic pressure on the sub passage 1105 side change in accordance with the engine rotational speed NE.

  Therefore, as a specific configuration for estimating the open / closed state of the first check valve 1118 provided in the first connection passage 1117, an operation map as shown in FIG. 6 is prepared in advance, and the operation map is opened and closed with reference to this operation map. A configuration for estimating the state can be employed.

  In the calculation map shown in FIG. 6, the hydraulic oil pressure PL of the hydraulic oil at the portion of the main passage 1104 to which the first connection passage 1117 is connected and the first check valve 1118 provided in the first connection passage 1117 are closed. The relationship between the engine rotational speed NE and the minimum value NEmin is shown. The lower the hydraulic pressure PL, the higher the minimum value NEmin. This is because, when a large amount of hydraulic oil is consumed in the transmission hydraulic circuit 120 and the hydraulic pressure PL is low, the first check valve is used unless the engine rotational speed NE is high and the discharge capacity of the main pump 1102 is high. This is based on the situation that 1118 does not close.

  The hydraulic pressure PL can be detected by a hydraulic pressure sensor, but the amount of hydraulic oil consumed in the shift hydraulic circuit 120 can be estimated and the hydraulic pressure PL can be estimated based on the estimated amount.

  The electronic control unit 20 calculates the value of the minimum value NEmin corresponding to the current hydraulic pressure PL with reference to such a calculation map, and compares the calculated minimum value NEmin with the current engine speed NE. Then, it is estimated that the first check valve 1118 is closed based on the current engine speed NE being equal to or higher than the minimum value NEmin.

  When the bypass switching valve 1180 is opened when it is estimated that the first check valve 1118 is closed in this way, a part of the hydraulic oil in the sub passage 1105 causes the primary regulator 1110 to pass through the bypass passage 1107. By detouring the flow, the same effect as (1) described in the first embodiment can be obtained.

In addition, it is possible to employ a configuration that estimates that the first check valve 1118 is closed based on the engine rotational speed NE being equal to or higher than the reference rotational speed NEst regardless of the hydraulic pressure PL. In the case of adopting such a configuration, in order to accurately estimate that the first check valve 1118 is closed, the value of the reference rotational speed NEst is set based on the results of experiments and the like performed in advance. It is desirable to set the check valve 1118 to a value larger than the minimum value of the engine rotational speed NE that is estimated to be surely closed.
(Second Embodiment)
Hereinafter, a second embodiment of the hydraulic device according to the present invention will be described with reference to FIG. The basic configuration of the second embodiment is the same as that of the first embodiment. As shown on the left side of FIG. 7, the second embodiment is more than the portion of the sub-passage 1105 to which the first connection passage 1117 is connected. An opening / closing switching valve 1140 for blocking this portion is provided in a portion on the downstream side and upstream of the portion where the bypass passage 1107 is connected. Therefore, in the following description, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof will be omitted. The components different from those in the first embodiment will be mainly described. FIG. 7 is a schematic diagram showing a schematic configuration of the hydraulic apparatus according to the second embodiment.

  As shown in FIG. 7, the spool valve of the open / close switching valve 1140 is always urged toward the valve closing side by the spring 1141 so as to block the sub passage 1105. The open / close switching valve 1140 is connected to a solenoid 1145 that applies a control hydraulic pressure to the spool valve based on a control command from the electronic control unit 20. As a result, in the open / close switching valve 1140, when the control hydraulic pressure is output from the solenoid 1145, the spool valve is driven to the valve opening side against the urging force of the spring 1141, and the sub-passage 1105 is the same. The open / close switching valve 1140 is in communication with the downstream portion. On the other hand, when the output of the control hydraulic pressure from the solenoid 1145 is stopped, the on / off switching valve 1140 is displaced to the valve closing side by the urging force of the spring 1141, and the sub passage 1105 is shut off. ing.

  In the hydraulic apparatus 100 of this embodiment provided with such an open / close switching valve 1140, when the open / close switching valve 1140 is opened, each of the hydraulic devices 100 according to the discharge capacity of the main pump 1102 is similar to the first embodiment. The check valves 1118 and 1128 are opened and closed, and the supply path of the hydraulic oil discharged from the sub pump 1103 is automatically switched.

  That is, when the discharge capacity of the main pump 1102 is less than the first level L1, the first check valve 1118 opens, and both the hydraulic oil discharged from the main pump 1102 and the hydraulic oil discharged from the sub pump 1103 are It is supplied to all of the hydraulic circuits 120, 130, and 140. On the other hand, when the discharge capacity of the main pump 1102 is equal to or higher than the first level L1 and lower than the second level L2, the first check valve 1118 is closed, and the hydraulic oil discharged from the sub pump 1103 is changed to the hydraulic pressure for shifting. Instead of being supplied to the circuit 120, the torque converter hydraulic circuit 130 and the lubricating hydraulic circuit 140 are supplied. When the discharge capacity of the main pump 1102 is equal to or higher than the second level L2, the second check valve 1128 is further closed, and the hydraulic oil discharged from the sub pump 1103 is transferred to the transmission hydraulic circuit 120 and the torque converter hydraulic circuit 130. It is supplied only to the lubricating hydraulic circuit 140 without being supplied.

  On the other hand, when the output of the control hydraulic pressure from the solenoid 1145 is stopped and the open / close switching valve 1140 is closed and switched to the shut-off state, the hydraulic pressure in the portion upstream of the open / close switching valve 1140 of the sub-passage 1105 is switched. Rises and the first check valve 1118 opens. As a result, the hydraulic oil discharged from the sub pump 1103 flows through the main passage 1104 together with the hydraulic oil discharged from the main pump 1102.

  In the hydraulic device 100 of this embodiment, when the hydraulic pressure required in each hydraulic circuit 120, 130, 140 increases rapidly, the output of the control hydraulic pressure from the solenoid 1145 is stopped, and the open / close switching valve 1140 is turned off. The valve is closed and switched to the shut-off state.

According to the second embodiment described above, in addition to the effect (1) described in the first embodiment, the following effect can be obtained.
(2) When the open / close switching valve 1140 is opened and in communication, the check valves 1118 and 1128 open and close according to the discharge capacity of the main pump 1102, and the supply path of hydraulic oil discharged from the sub pump 1103 is Switch automatically. On the other hand, when the on / off switching valve 1140 is closed and shut off, the hydraulic pressure in the upstream portion of the sub-passage 1105 with respect to the on / off switching valve 1140 increases and the first check valve 1118 opens. Then, the hydraulic oil discharged from the sub pump 1103 flows through the main passage 1104 together with the hydraulic oil discharged from the main pump 1102. In other words, by closing the on-off switching valve 1140 and closing it, the hydraulic pressure on the sub passage 1105 side of the first check valve 1118 is quickly raised to open the first check valve 1118 and discharge from the sub pump 1103. The hydraulic oil to be used can be introduced into the main passage 1104. That is, by closing the on-off switching valve 1140 and shutting it off, the hydraulic pressure of the hydraulic oil supplied quickly is increased when the hydraulic pressure required in each hydraulic circuit 120, 130, 140 increases rapidly. Will be able to.

The elements that can be changed in common with the first embodiment and the second embodiment are as follows.
As an example of the bypass path, the bypass path 1107 that connects the upstream and downstream of the primary regulator 1110 is illustrated. On the other hand, when the hydraulic pressure at the upstream side of the secondary regulator 1120 in the sub passage 1105 increases and the load applied to the driving of the sub pump 1103 may increase, the upstream and downstream of the secondary regulator 1120 are connected. It is also possible to employ a configuration in which a bypass path to be connected is provided. In addition, a configuration in which a bypass path that connects the upstream of the primary regulator 1110 and the downstream of the secondary regulator 1120 may be employed.

  In each of the above embodiments, the hydraulic device 100 that supplies hydraulic oil to the continuously variable transmission 10 mounted on the vehicle is illustrated as an embodiment of the present invention, but the hydraulic device according to the present invention is a continuously variable transmission. It is not limited to the hydraulic device. In addition, the present invention can also be applied to a hydraulic device that supplies hydraulic oil to a valve mechanism of an internal combustion engine or a hydraulic device that is combined with an internal combustion engine other than a vehicle internal combustion engine.

DESCRIPTION OF SYMBOLS 10 ... Continuously variable transmission, 11 ... Torque converter, 12 ... Input shaft, 13 ... Lock-up clutch, 14 ... Output shaft, 15 ... Primary pulley, 16 ... Secondary pulley, 17 ... Belt, 18 ... Output shaft, 19 ... Forward Reverse switching mechanism, 20 ... electronic control device, 21 ... accelerator position sensor, 22 ... vehicle speed sensor, 23 ... rotational speed sensor, 100 ... hydraulic device, 110 ... hydraulic supply circuit, 120 ... hydraulic circuit for shifting, 130 ... for torque converter Hydraulic circuit, 140 ... Lubrication hydraulic circuit, 1101 ... Oil pan, 1102 ... Main pump, 1103 ... Sub pump, 1104 ... Main passage, 1105 ... Sub passage, 1106 ... Drain passage, 1107 ... Detour passage, 1110 ... Primary regulator, 1111 ... Spring, 1112 ... Feedback path, 1113 ... Mei Port 1114 ... Sub port 1115 ... Linear solenoid 1117 ... First connecting passage 1118 ... First check valve 1120 ... Secondary regulator 1121 ... Spring 1122 ... Feedback passage 1123 ... Main port 1124 ... Sub port 1125 ... Linear solenoid, 1127 ... second connection passage, 1128 ... second check valve, 1130 ... lubrication regulator, 1131 ... spring, 1132 ... feedback passage, 1133 ... drain port, 1134 ... sub port, 1137 ... third connection passage, 1138 ... first 3 check valve, 1140 ... switching valve, 1141 ... spring, 1145 ... solenoid, 1170 ... bypass regulator, 1171 ... spring, 1172 ... feedback path, 1180 ... bypass off Valve, 1181 ... spring, 1185 ... solenoid.

Claims (9)

Engine driven main pump and sub pump, main passage for supplying hydraulic oil discharged from the main pump to the hydraulic demand section, sub passage connected to the sub pump, and supply to the hydraulic demand section through the main passage A regulator that adjusts the hydraulic pressure of the hydraulic fluid in the main passage and the hydraulic pressure of the hydraulic fluid in the sub passage, and the main passage and the sub passage from the regulator. And a check valve that is provided in the connection passage and allows only the flow of hydraulic oil from the sub-passage side to the main passage side. As the capacity increases, the check valve closes, and the supply path for the hydraulic oil discharged from the sub-pump automatically depends on the discharge capacity of the main pump. In the hydraulic system to switch to, the
A bypass path that bypasses the regulator and connects a portion upstream of the regulator in the sub-passage and a portion downstream of the regulator in the sub-passage, and is provided in the bypass passage in the sub-passage. A hydraulic device comprising: an on-off valve that opens as the hydraulic pressure of hydraulic oil in a portion upstream of the regulator increases. The hydraulic device according to claim 1,
The on-off valve is a check valve that includes a valve body and a biasing member that biases the valve body in a valve closing direction, and the bypass is provided when the check valve provided in the connection passage is closed. A hydraulic device that opens when hydraulic pressure of hydraulic oil in a portion upstream of the on-off valve in the passage is higher than hydraulic pressure of hydraulic oil in a portion downstream of the open / close valve. The hydraulic device according to claim 1,
The on-off valve includes a valve body, an urging member that urges the valve body in a valve closing direction, and a feedback passage that applies hydraulic pressure of hydraulic oil in a portion upstream of the on-off valve in the bypass passage to the valve body. A hydraulic device that opens as the hydraulic pressure of hydraulic fluid in a portion upstream of the on-off valve in the bypass passage increases. The hydraulic device according to claim 1,
The on-off valve is a switching valve that is switched between a valve opening state and a valve closing state by a control hydraulic pressure output from a solenoid,
The hydraulic apparatus includes an open / close state estimation unit that estimates an open / close state of a check valve provided in the connection passage, and the check valve provided in the connection passage is closed by the open / close state estimation unit. The hydraulic apparatus, wherein the solenoid is controlled to open the on-off valve when estimated. The hydraulic device according to claim 4, wherein
The open / close state estimation means estimates an open / close state of a check valve provided in the connection passage based on hydraulic pressure and engine rotation speed of hydraulic oil at a portion of the main passage to which the connection passage is connected. Hydraulic system. The hydraulic device according to claim 5,
The open / close state estimation means indicates a relationship between hydraulic pressure of hydraulic oil at a portion of the main passage to which the connection passage is connected and a minimum value of an engine rotation speed at which a check valve provided in the connection passage is closed. The minimum value corresponding to the current hydraulic pressure of the hydraulic fluid in the portion of the main passage to which the connecting passage is connected is calculated with reference to the calculation map, and the lowest value and the current engine speed are calculated. The hydraulic device is characterized by estimating that the check valve provided in the connecting passage is closed based on the fact that the current engine speed is equal to or higher than the lowest value. The hydraulic device according to claim 4, wherein
The opening / closing state estimation means estimates that a check valve provided in the connection passage is closed based on an engine rotational speed being equal to or higher than a reference rotational speed. An opening / closing switching valve is further provided in a portion downstream of the portion where the connecting passage is connected in the sub passage and upstream of the portion where the bypass passage is connected. A shut-off state in which the supply of hydraulic oil to the portion downstream of the opening / closing switching valve in the sub passage is blocked, and the supply of hydraulic oil to the portion downstream of the opening / closing switching valve in the sub passage is permitted. The hydraulic apparatus according to any one of claims 1 to 7, wherein the hydraulic apparatus is switched to a communication state. In the hydraulic apparatus as described in any one of Claims 1-8,
The on-off valve is opened when the amount of displacement of the regulator toward the valve opening side is maximized and the opening area of the sub port through which the hydraulic oil flowing through the sub passage passes is maximized. Hydraulic device characterized.

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