JP5831680B2 - Booster - Google Patents

Description

  The present invention relates to a booster used for a clutch mechanism.

  As a prior art, for example, an automatic clutch engaging / disengaging device is known (for example, refer to Patent Document 1).

  In this automatic clutch stage side device, a motor driven single piston type actuator is interposed as a booster between the hydraulic pump and the clutch.

Japanese Patent Laid-Open No. 11-063017

  However, in such a conventional case, an increase in the size of the motor and the speed reduction mechanism is unavoidable in order to achieve both high capacity, high pressure and high responsiveness.

  Along with this, there is a problem that mountability to a transmission or the like deteriorates.

  The present invention has been made in view of such a conventional problem, and an object of the present invention is to provide a booster capable of miniaturization while achieving high performance.

According to the first aspect of the present invention, the drive unit and the control unit are separated in the axial direction by the partition plate, and the drive unit is connected to the motor via the reduction gear and is connected to the motor. A screw member that reciprocates in the axial direction by rotational drive, and the control unit is attached to the screw member and reciprocates in the axial direction, and internal oil is pressurized by the primary piston. A primary side oil chamber, a secondary side oil chamber to which oil from the primary side oil chamber is supplied via a communication path, and supply of oil from the primary side oil chamber to the secondary side oil chamber. Accordingly, a switching mechanism that closes the communication path, a secondary piston that retreats and pressurizes the oil in the secondary oil chamber by receiving the hydraulic pressure in the primary oil chamber, and the oil in the secondary oil chamber Output port for output And an input port through which oil flows is provided in the primary side oil chamber, and the input port is located on the tip side of the primary side piston in a state in which the primary side piston is retracted to the partition plate side. The primary side oil chamber is communicated with the primary side oil chamber, while the primary side piston is advanced to a predetermined position, the communication with the primary side oil chamber on the tip side of the primary side piston is blocked. An apparatus is provided.
  According to the second aspect of the present invention, the primary side piston that is actuated by applying a driving force, the primary side oil chamber in which the internal oil is pressurized by the primary side piston, and the primary side oil chamber A secondary-side oil chamber to which oil is supplied via a communication path; a switching mechanism that closes the communication path with the supply of oil from the primary-side oil chamber to the secondary-side oil chamber; and the primary-side Receiving a hydraulic pressure in the oil chamber and retreating to pressurize the oil in the secondary oil chamber, and an output port for outputting the oil in the secondary oil chamber, and the secondary side An end opening portion of the communication passage formed in the piston is opened on the side surface of the secondary piston, and a step portion communicating with the primary oil chamber is recessed in a portion of the cylinder inner surface facing the end opening portion. The secondary piston In the backward movement, the end opening is changed from a communicating state facing the stepped portion to a closed state in which the end opening is closed facing a general portion of the cylinder inner surface. A booster is provided.

  That is, when driving force is applied and the primary piston is operated in the forward direction, the oil in the primary oil chamber is pressurized, and after the oil is supplied to the secondary oil chamber via the communication path, the output port is Via, for example, an actuator such as a clutch. Accordingly, the oil is supplied to the actuator, and the supply hydraulic pressure is gradually increased.

  The communication path is closed with the supply of oil from the primary oil chamber to the secondary oil chamber. Then, the hydraulic pressure in the primary oil chamber raised by the primary side piston acts as a force for retreating the secondary side piston. The secondary piston thus retracted pressurizes the oil in the secondary oil chamber, so that the hydraulic pressure supplied to the actuator via the output port is increased.

  Thus, when the operation of the primary piston is started, the oil corresponding to the operation amount of the primary piston is supplied to the actuator, and from the time when the communication path is closed, the operation amount of the secondary piston is increased. The corresponding hydraulic pressure is supplied to the actuator.

Was set pressure receiving area of the primary-side oil chamber side of the front Symbol secondary piston to be larger than the pressure receiving area of the secondary-side oil chamber side.

  That is, since the pressure receiving area on the primary oil chamber side is set larger than the pressure receiving area on the secondary oil chamber side, it is possible to increase the pressure on the secondary oil chamber side according to Pascal's principle. Become.

Communicating an end opening portion of the communicating passage formed in the previous SL secondary piston with an opening on the side surface of the secondary piston, the primary-side oil chamber to the site of the inner surface of the cylinder in which the end portion opening faces When the secondary piston moves backward, the end opening is closed to face the general part of the cylinder inner surface from the communication state where the end opening faces the step. Configured to change to a closed state.

  That is, when the pressurization of the primary oil chamber by the primary piston is started, the oil in the primary oil chamber that has flowed in between the side surface of the secondary piston and the stepped portion of the cylinder inner surface is It flows through the communicating path through an end opening that opens in the side surface of the side piston. And this oil is supplied to the said secondary side oil chamber via the said communicating path.

  Next, when the secondary piston is retracted as the oil pressure in the primary oil chamber increases, the end opening is closed by facing a general portion of the cylinder inner surface, and the communication passage is interposed. Supply to the secondary oil chamber is shut off.

  Thereby, the switching mechanism mentioned above is comprised.

It provided a return spring for urging the front Symbol secondary piston toward the primary-side oil chamber side.

  That is, the biasing force of the return spring is applied to the secondary piston in addition to the pressure from the secondary oil chamber.

  According to a fifth aspect of the present invention, there is provided a pressure regulating mechanism that absorbs a hydraulic shock generated in the secondary oil chamber.

  As a result, the impact of hydraulic pressure that can occur in the secondary oil chamber is reduced.

  Furthermore, in the booster of claim 6, the secondary piston and the pressure regulating mechanism are arranged in parallel.

  Thereby, compared with the case where the said secondary side piston and the said pressure regulation mechanism are arrange | positioned in series, the length dimension as a whole is suppressed.

  In addition, in the booster of the seventh aspect, the secondary piston is arranged at the center, and the ring-shaped pressure regulating mechanism is arranged on the outer peripheral portion of the secondary piston.

  Thereby, the outer peripheral space of the secondary piston is effectively used.

  In the booster according to the eighth aspect of the invention, the pressure regulating mechanism is arranged at the center, and the ring-shaped secondary piston is arranged on the outer periphery of the pressure regulating mechanism.

  Thereby, the outer peripheral space of the pressure regulating mechanism is effectively used.

  Furthermore, in the booster according to a ninth aspect, the communication path is provided in the pressure regulating mechanism.

  Thereby, the function of the said communicating path can be added to the said pressure regulation mechanism.

As described above, in the booster of the present invention , at the start of the operation of the primary piston, oil corresponding to the operation amount of the primary piston can be supplied to the actuator, and from the time when the communication path is closed. Can supply the hydraulic pressure according to the operation amount of the secondary side piston to the actuator.

  In this way, by dividing the roles of oil supply and oil pressure supply, priority is given to oil supply when oil supply is required and oil supply when oil pressure is required. it can. For this reason, compared with the case where the supply of oil and the supply of hydraulic pressure must be performed by a single piston, it becomes easier to supply the capacity and pressure as required, and the motor and the speed reduction mechanism are enlarged. The response to the request can be improved without any problems.

  Thereby, since size reduction and performance improvement can be achieved, the mounting property to a transmission etc. can be improved.

Receiving area of the prior SL primary side oil chamber side, since it is set larger than the pressure receiving area of the secondary-side oil chamber side, by Pascal's principle, possible to increase the pressure at the secondary side oil chamber side Can do.

By using the pre-Symbol secondary piston, it is possible to configure the switching mechanism described above.

  Thereby, the secondary piston can be effectively used.

Before SL secondary piston biasing force of the return spring is applied in addition to the pressure from the secondary oil chamber.

  For this reason, the hydraulic pressure of the secondary piston can be adjusted by changing the urging force of the return spring.

  In the booster according to the fifth aspect, the impact of hydraulic pressure that can occur in the secondary oil chamber can be reduced.

  Thereby, the bad influence resulting from an impact pressure can be suppressed.

  Furthermore, in the booster of claim 6, the secondary piston and the pressure regulating mechanism are arranged in parallel, thereby comparing with the case where the secondary piston and the pressure regulating mechanism are arranged in series. Thus, the length dimension can be suppressed, which can contribute to downsizing.

  In addition, in the booster of claim 7, the secondary piston is disposed around the center, and the ring-shaped pressure regulating mechanism is disposed on the outer peripheral portion of the secondary piston. Effective utilization of the outer peripheral space of the secondary piston can be achieved.

  In the booster of claim 8, the pressure regulating mechanism is arranged around the center, and the ring-shaped secondary piston is disposed on the outer periphery of the pressure regulating mechanism, so that the pressure regulating mechanism is Effective use of the outer peripheral space can be achieved.

  Furthermore, in the booster according to the ninth aspect, the function by the pressure regulating mechanism and the function by the communication path can be obtained by providing the communicating path in the pressure regulating mechanism.

It is explanatory drawing which shows 1st embodiment of this invention. It is sectional drawing which shows the embodiment. It is explanatory drawing which shows operation | movement of the embodiment. It is explanatory drawing which shows the pressure regulation mechanism of the embodiment. It is explanatory drawing which shows arrangement | positioning of the embodiment. It is explanatory drawing which shows the hydraulic pressure raise operation | movement of the embodiment. It is explanatory drawing which shows the data of each place at the time of the hydraulic pressure raise operation | movement of the embodiment. It is explanatory drawing which shows the hydraulic pressure reduction operation | movement of the embodiment. It is explanatory drawing which shows the data of each place at the time of the hydraulic pressure reduction operation | movement of the embodiment. It is explanatory drawing which shows the function of the embodiment. It is explanatory drawing which shows 2nd embodiment of this invention. It is explanatory drawing which shows 3rd embodiment of this invention. It is explanatory drawing which shows 4th embodiment of this invention. It is explanatory drawing which shows 5th embodiment of this invention.

  (First embodiment)

  Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.

  FIG. 1 is a diagram showing a booster 1 according to the present embodiment. The booster 1 is a device that controls, for example, a clutch mounted on a vehicle.

  As shown in the upper right in FIG. 1, the booster 1 is formed in a cylindrical shape, and its A cross section, B cross section, and C cross section are shown in FIG. As shown in FIG. 2, the booster 1 is provided with a drive unit 12 on the proximal end side with the partition plate 11 as a boundary, and a control unit 13 on the distal end side thereof.

  The driving unit 12 includes a bottomed cylindrical casing 21 that forms a closed space together with the partition plate 11, and a DC motor 22 constituting a driving source is provided in the casing 21. The rotary shaft 23 of the DC motor 22 is connected to a trapezoidal screw 25 via a reduction gear 24, and the trapezoidal screw 25 is screwed into the partition plate 11. The tip of the trapezoidal screw 25 extends through the partition plate 11 to the control unit 13 side, and rotates toward the control unit 13 by rotating and moving forward with the DC motor 22. The amount is variable.

  The outer peripheral portion of the control unit 13 is constituted by a cylindrical flow cylinder 31, and the flow cylinder 31 is fixed in a state in which its proximal end is in close contact with the partition plate 11, and its distal end is a lid portion. It is closed at 32.

  The trapezoidal screw 25 extends at the base end portion of the flow rate cylinder 31, and a flow rate piston 41 constituting a primary piston is provided at the distal end of the trapezoidal screw 25. As a result, the flow rate piston 41 is configured to operate with the driving force from the DC motor 22 applied thereto.

  At this time, the flow piston 41 is configured to move back and forth with the rotation of the reduction gear 24 and the trapezoidal screw 25. For this reason, even if the DC motor 22 is de-energized, it is provided with a self-holding function for holding its moving position, and an energy saving effect is obtained.

  The flow piston 41 is formed in a thin cylindrical shape, and its outer dimension is set to a size that matches the inner diameter of the flow cylinder 31. An O-ring 51 is provided on the outer peripheral surface of the flow rate piston 41, and the O-ring 51 is configured to come into sliding contact with the inner peripheral surface of the flow rate cylinder 31 when the flow rate piston 41 moves back and forth. ing.

  An input port 61 through which oil flows is provided at the base end of the flow cylinder 31, and the input port 61 communicates with the front end side of the flow piston 41 in a state where the flow piston 41 is most retracted. On the other hand, when the flow rate piston 41 moves forward to a predetermined position, the communication state between the input port 61 and the front end side of the flow rate piston 41 is cut off.

  As shown in FIGS. 1 and 2, a cylindrical pressure-increasing cylinder 71 is provided on the distal end side of the flow rate cylinder 31. The pressure-increasing cylinder 71 is disposed on the lower side in FIG. 2, and a part of the pressure-increasing cylinder 71 on the lower side in FIG.

  As shown in FIG. 2, a tip extending portion 81 extending toward the center is formed in a ring shape at the tip of the pressure increasing cylinder 71, and from the inner edge of the tip extending portion 81, a cylinder A cylindrical small-diameter portion 82 extends toward the base end side. Thus, a spring holding portion 83 is formed between the small diameter cylindrical portion 82 and the pressure increasing cylinder 71, and one end portion of a return spring 84 formed of a coil spring is held in the spring holding portion 83. ing.

  The small diameter cylindrical portion 82 extends to a midway portion of the pressure increasing cylinder 71, and a small diameter portion 91 composed of the small diameter cylindrical portion 82 is provided at the distal end portion of the pressure increasing cylinder 71, and also on the proximal end side. A large diameter portion 92 is formed.

  In the pressure increasing cylinder 71, a pressure increasing piston 101 constituting a secondary side piston is fitted, and the pressure increasing piston 101 has a columnar head 102 fitted in the large diameter portion 92 and A small-diameter columnar neck 103 fitted into the small-diameter portion 91 is formed in a T-shaped cross section.

  The peripheral surface of the neck portion 103 is configured to be in sliding contact with a seal ring 111 provided on the inner surface of the small diameter cylindrical portion 82, and the outer peripheral surface of the head portion 102 is provided with the pressure increasing cylinder 71. A pair of O-rings 113, 113 that are in sliding contact with the cylinder inner surface 112 are provided.

  As a result, the flow cylinder 31 is partitioned with the boosting piston 101 as a boundary, and a primary oil chamber 121 is formed on the base end side of the boosting piston 101. Further, a secondary oil chamber 122 is formed at the tip side of the pressure increasing piston 101, and the secondary oil chamber 122 has a communication portion 123 provided at the tip of the pressure increasing cylinder 71. Via the pressure control chamber 124 provided on the side of the pressure-increasing cylinder 71.

  The other end of the return spring 84 is in contact with the back surface of the head portion 102 of the pressure-increasing piston 101, and the pressure-increasing piston 101 is brought into contact with the primary oil chamber 121 side by the return spring 84 when retreating. It is comprised so that the urging | biasing force which aimed at may be provided.

  The pressure receiving area 132 on the primary oil chamber 121 side formed by the head end surface 131 of the head 102 of the pressure increasing piston 101 is configured by the neck end surface 133 at the base end of the neck 103 of the pressure increasing piston 101. The pressure is set to be larger than the pressure receiving area 134 on the secondary oil chamber 122 side.

  As a result, as shown in FIG. 3, the flow-cylinder-side thrust G acting on the pressure-increasing piston 101 in the distal direction is “the hydraulic pressure in the primary-side oil chamber 121 (flow-rate piston-side hydraulic pressure) × The pressure receiving area 132 on the primary oil chamber 121 side is configured.

  On the other hand, the pressure-increasing cylinder side thrust acting toward the base end direction with respect to the pressure-increasing piston 101 is “(hydraulic pressure in the secondary oil chamber 122 (flow cylinder hydraulic pressure) × the secondary oil chamber 122”. Side pressure receiving area 134) D + (return spring thrust) E + (area of the back surface of the head 102 of the pressure-increasing piston 101 (return spring chamber area + return spring pressure)) F ".

  As shown in FIG. 2, the pressure-increasing piston 101 is formed with a communication passage 141 that communicates the primary-side oil chamber 121 and the secondary-side oil chamber 122. Formed in an L-shaped cross section by a rectilinear portion 142 extending along the center line of the neck portion 103 and a bent portion 143 that is bent laterally from the rectilinear portion 142 and extends in the radial direction of the head portion 102. Has been.

  As a result, the end opening 151 on one end side of the communication passage 141 opens on the end surface of the neck 103 of the pressure-increasing piston 101 and the end opening 152 on the other end side increases in the pressure-increasing pressure. The piston 101 opens to the side surface of the head portion 102, and the opening position of the end opening 152 is set between the O-rings 1113 and 113.

  A stepped portion 161 communicating with the primary-side oil chamber 121 is provided at a base end portion of the pressure-increasing cylinder 71 at a portion of the cylinder inner surface 112 of the pressure-increasing cylinder 71 facing the end opening 152 on the other end side. When the end opening 152 faces the stepped portion 161, a communication state 162 is formed in which the primary oil chamber 121 communicates with the communication passage 141. ing. On the other hand, when the pressure-increasing piston 71 moves backward and the end opening 152 faces the general part 163 of the cylinder inner surface 112, the end opening 152 forms the general part 163 and both the O-rings 113. , 113 and are configured to form a closed state 164 in which the communication path 141 is closed as shown in FIG.

  As shown in FIG. 1, the pressure control chamber 124 is formed of a cylindrical space, and a part of the surrounding wall 171 surrounding the pressure control chamber 124 is as shown in FIG. The flow cylinder 31 and the pressure increasing cylinder 71 are configured. The base end of the surrounding wall 171 is closed by a closing member 172, and the pressure control chamber 124 closed by the closing member 172 communicates with the outside through a drain port (not shown). ing.

  A pressure regulating spring 181 is accommodated in the pressure control chamber 124, and one end of the pressure regulating spring 181 is in contact with the closing member 172. A cylindrical valve body 182 is supported on the other end of the pressure adjusting spring 181, and an O-ring 183 provided on the outer peripheral surface of the valve body 182 is in sliding contact with the surrounding wall 171. It is configured.

  Accordingly, when a hydraulic shock is applied to the secondary oil chamber 122, the valve body 182 is retracted to absorb the shock. As shown in FIG. A pressure adjusting mechanism 191 for absorption is configured. Further, the pressure adjusting mechanism 191 is arranged in parallel with the pressure increasing piston 101 as shown in FIG.

  As shown in FIG. 2, the pressure control chamber 124 communicates with an output port 201 provided at the tip of the flow rate cylinder 31, and the output port 201 is connected to a clutch as an actuator. It is configured.

  FIG. 6 is an explanatory diagram showing an operation of advancing the flow rate piston 41 by the DC motor 22 to increase the pressure supplied from the output port 201 to the clutch 211, and FIG. 7 is an operation state of each part at that time. The hydraulic pressure output from the output port 201 and the amount of discharged oil are also shown.

  That is, when the flow rate piston 41 is most retracted, the input port 61 and the output port 201 are communicated, and the original pressure, that is, the hydraulic pressure becomes “0” (S1). Then, as the flow rate piston 41 advances, the oil in the primary side oil chamber 121 is pressurized, and the oil is supplied from the output port 201 via the communication path 141, and the pressure increasing piston 101 moves backward. (S2 to S3) Eventually, the communication path 141 is closed (S4).

  In this state, when the flow rate piston 41 is further advanced, the pressure-increasing piston 101 that has received the oil pressure in the primary oil chamber 121 moves backward to pressurize the oil in the secondary oil chamber 122. The hydraulic pressure supplied from the output port 201 increases (S5). Thereby, the clutch 211 can be reliably met.

  On the other hand, FIG. 8 is an explanatory view showing an operation of reducing the pressure supplied from the output port 201 to the clutch 211 by retreating the flow rate piston 41 by the DC motor 22, and FIG. The operating state, the hydraulic pressure output from the output port 201, and the amount of discharged oil are shown.

  That is, in the state where the flow rate piston 41 is most advanced, the hydraulic pressure supplied from the output port 201 is the maximum (SB1), and the clutch 211 is reliably met.

  When the flow rate piston 41 is retracted from this state, the pressure-increasing piston 101 starts to retract (SB2), and the communication path 141 is eventually opened (SB3).

  Further, when the flow rate piston 41 is retracted, the oil supplied to the clutch 211 returns to the primary oil chamber 121 via the communication path 141 (SB4), and in the state where the flow rate piston 41 is most retracted, The output port 201 and the input port 61 communicate with each other, and the original pressure, that is, the hydraulic pressure becomes “0” (SB4).

  Thus, as shown in FIG. 10, the flow piston 41 can realize a high flow rate at a low pressure, and the pressure increase piston 101 can realize a high pressure supply at a low flow rate.

  During this time, the supply of oil from the primary side oil chamber 121 to the secondary side oil chamber 122 is continued, while the pressure-increasing piston 101 retreats and the flow passage piston 41 is controlled when the communication passage 141 is closed. From the normal high flow state, the pressure increasing piston 101 is switched to the dominant pressure increasing state. Thereby, the switching mechanism 221 of the present invention is configured.

  More specifically, as shown in FIG. 2, when the pressurization of the primary oil chamber 121 by the flow rate piston 41 is started, a gap between the side surface of the pressure increasing piston 101 and the step 161 of the cylinder inner surface 112 is established. The oil in the primary oil chamber 121 that has flowed into the flow passage flows into the communication passage 141 through the end opening 152 that opens in the side surface of the pressure-increasing piston 101. The oil is supplied to the secondary oil chamber 122 through the communication path 141.

  Next, when the pressure-increasing piston 101 further retracts as the hydraulic pressure in the primary oil chamber 121 increases, the end opening 152 is closed by facing the general portion 163 of the cylinder inner surface 112, The supply to the secondary oil chamber 122 is cut off via the communication path 141.

  Thereby, the switching mechanism 221 mentioned above is comprised.

  In the present embodiment according to the above configuration, when the operation of the flow piston 41 is started, oil corresponding to the operation amount of the flow piston 41 can be supplied to the clutch 211, and the communication passage 141 is closed. The hydraulic pressure corresponding to the operation amount of the pressure increasing piston 101 can be supplied to the clutch 211.

  In this way, by dividing the roles of oil supply and oil pressure supply, priority is given to oil supply when oil supply is required and oil supply when oil pressure is required. it can.

  For this reason, compared with the case where the supply of oil and the supply of hydraulic pressure must be performed by a single piston, it becomes easier to supply the capacity and pressure as required, and the DC motor 22 and the speed reduction mechanism are made larger. Responsiveness to the request can be improved without making it.

  Thereby, since size reduction and performance improvement can be achieved, the mounting property to a transmission can be improved.

  In addition, since the pressure receiving area 132 on the primary oil chamber 121 side of the boosting piston 101 is set larger than the pressure receiving area 134 on the secondary oil chamber 122 side, the secondary side is based on Pascal's principle. The pressure on the oil chamber 122 side can be increased.

  Further, since the above-described switching mechanism 221 is configured using the pressure increasing piston 101, the pressure increasing piston 101 can be effectively used.

  Here, in addition to the pressure from the secondary side oil chamber 122, the urging force of the return spring 84 is applied to the pressure increasing piston 101.

  For this reason, the hydraulic pressure of the booster piston 101 can be adjusted by changing the urging force of the return spring 84.

  The booster 1 is provided with a pressure adjusting mechanism 191 that absorbs a hydraulic shock generated in the secondary oil chamber 122.

  For this reason, the impact of hydraulic pressure that can occur in the secondary oil chamber 122 can be reduced. Therefore, adverse effects caused by the impact pressure can be suppressed.

  Furthermore, in this embodiment, the pressure increasing piston 101 and the pressure regulating mechanism 191 are arranged in parallel.

For this reason, compared with the case where the said pressure increase piston 101 and the said pressure regulation mechanism 191 are arrange | positioned in series, the length dimension as a whole can be restrained and it can contribute to size reduction.

  (Second embodiment)

  FIG. 11 is a diagram showing the second embodiment, where the same or equivalent parts as those of the first embodiment are denoted by the same reference numerals and the description thereof is omitted, and only different parts are explained. To do.

  That is, in the booster 1001 according to the present embodiment, the booster cylinder 71 and the booster piston 101 are arranged at the center of the booster 1001, and a ring shape is formed on the outer periphery of the booster cylinder 71. The pressure adjusting mechanism 191 is disposed.

Thereby, the effective utilization of the outer peripheral part space of the said pressure increase piston 101 can be aimed at.

  (Third embodiment)

  FIG. 12 is a diagram showing the third embodiment, where the same or equivalent parts as those of the first embodiment are denoted by the same reference numerals and the description thereof is omitted, and only different parts are explained. To do.

  That is, in the booster 1101 according to the present embodiment, the pressure regulating mechanism 191 is disposed at the center of the booster 1101, and the pressure-increasing cylinder 71 in a ring shape is formed on the outer periphery of the pressure regulating mechanism 191. In addition, the pressure-increasing piston 101 is disposed.

Thereby, the effective utilization of the outer peripheral space of the pressure adjusting mechanism 191 can be achieved.

  (Fourth embodiment)

  FIG. 13 is a diagram showing the fourth embodiment, where the same or equivalent parts as those of the first embodiment are denoted by the same reference numerals and the description thereof is omitted, and only different parts are explained. To do.

  That is, in the booster 1201 according to the present embodiment, the communication path 141 is provided in the pressure regulating mechanism 191.

  More specifically, the pressure control chamber 124 is provided at the center of the booster 1201, and the pressure control chamber 124 is surrounded by the surrounding wall 171. The pressure control chamber 124 accommodates the pressure adjusting spring 181, and one end of the pressure adjusting spring 181 extends inward from the end of the surrounding wall 171. Supported by the part 1211.

  The other end of the pressure regulating spring 181 is in contact with a pressure regulating piston 1221 that constitutes the valve body 182, and the pressure regulating piston 1221 is biased toward the lid portion 32.

  The pressure adjusting piston 1221 is formed with the communication passage 141, and an end opening 152 of the communication passage 141 is open to the circumferential surface of the pressure adjusting piston 1221.

  Thus, when the pressure regulating piston 1221 moves in the proximal direction due to the oil pressure in the secondary side oil chamber 122, the end opening 152 of the communication path 141 faces the inner surface of the surrounding wall 171. Thus, the retraction of the pressure-increasing piston 101 is promoted, and the oil pressure in the secondary oil chamber 122 can be increased.

In this Embodiment which concerns on the above structure, since the said communication path 141 was provided in the said pressure regulation mechanism 191, the function of the said pressure regulation mechanism 191 and the function of the said communication path 141 can be obtained simultaneously.

  (Fifth embodiment)

  FIG. 14 is a diagram showing the fifth embodiment, where the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals and the description thereof is omitted, and only different parts are explained. To do.

That is, in the booster 1301 according to the present embodiment, the communication path 141 is provided in the pressure regulating mechanism 191.

  More specifically, a cylindrical pressure regulating piston 1311 is held in the pressure control chamber 124 so as to be movable in the axial direction, and the large diameter portion 1312 of the pressure regulating piston 1311 and the pressure regulating piston 1311. A pressure regulating spring 181 is disposed between the ring-shaped holding portion 1313 and the ring-shaped holding portion 1313.

  The pressure regulating piston 1311 is formed with the communication passage 141, and an end opening 152 of the communication passage 141 is formed on the peripheral surface of the large diameter portion 1312.

  The step 161 is formed on the outer peripheral surface of the pressure increasing cylinder 71 facing the end opening 152, and the primary oil chamber 121 and the secondary oil chamber are connected via the communication passage 141. The communication state with 122 can be secured.

  On the other hand, when the pressure adjusting piston 1311 is moved in the proximal direction by the oil pressure in the secondary oil chamber 122, the end opening 152 of the communication path 141 is generally disposed on the outer peripheral surface of the pressure increasing cylinder 71. It is configured so as to be opposed to the portion, and thereby, the backward movement of the pressure-increasing piston 101 is promoted, and the hydraulic pressure in the secondary side oil chamber 122 can be increased.

  Even in the present embodiment having the above configuration, since the communication path 141 is provided in the pressure adjusting mechanism 191, the function of the pressure adjusting mechanism 191 and the function of the communication path 141 can be obtained simultaneously.

1 Booster 22 DC Motor 41 Flow Piston 84 Return Spring 101 Booster Piston 112 Cylinder Inner Surface 121 Primary Side Oil Chamber 122 Secondary Side Oil Chamber 141 Communication Path 152 End Opening 161 Stepped Part 162 Communication State 163 General Part 164 Closed State 191 Pressure regulating mechanism 201 Output port 221 Switching mechanism 1001 Booster device 1101 Booster device 1201 Booster device 1301 Booster device

Claims (9)

Including a drive unit and a control unit separated in the axial direction by a partition plate;
The drive unit includes a motor and a screw member that is coupled to the motor via a reduction gear and reciprocates in the axial direction by rotational driving of the motor.
The control unit is attached to the screw member and reciprocally moves in the axial direction ;
A primary oil chamber in which internal oil is pressurized by the primary piston;
A secondary-side oil chamber to which oil from the primary-side oil chamber is supplied via a communication path;
A switching mechanism that closes the communication path with the supply of oil from the primary oil chamber to the secondary oil chamber;
Receiving a hydraulic pressure in the primary side oil chamber, retreating and pressurizing the oil in the secondary side oil chamber;
An output port for outputting oil in the secondary oil chamber;
Equipped with a,
The primary side oil chamber is provided with an input port through which oil flows,
The input port communicates with the primary-side oil chamber on the tip side from the primary-side piston with the primary-side piston retracted toward the partition plate, while the primary-side piston has advanced to a predetermined position. A booster characterized in that communication with the primary oil chamber on the tip side of the primary piston is blocked . A primary piston that is actuated by a driving force;
A primary oil chamber in which internal oil is pressurized by the primary piston;
A secondary-side oil chamber to which oil from the primary-side oil chamber is supplied via a communication path;
A switching mechanism that closes the communication path with the supply of oil from the primary oil chamber to the secondary oil chamber;
Receiving a hydraulic pressure in the primary side oil chamber, retreating and pressurizing the oil in the secondary side oil chamber;
An output port for outputting oil in the secondary oil chamber;
Equipped with a,
The end opening portion of the communication passage formed in the secondary piston is opened to the side surface of the secondary piston, and the primary oil chamber communicates with a portion of the cylinder inner surface facing the end opening portion. A stepped portion is provided, and when the secondary piston moves backward, the end opening is closed facing the general portion of the inner surface of the cylinder from the communication state where the end opening faces the stepped portion. A booster that is configured to change to a closed state . The booster according to claim 2, further comprising a return spring that urges the secondary piston toward the primary oil chamber. According to any one of claims 1 to 3, characterized in that setting the pressure receiving area of the primary-side oil chamber side of the secondary piston to be larger than the pressure receiving area of the secondary-side oil chamber side Boost device.   The booster according to any one of claims 1 to 4, further comprising a pressure adjusting mechanism that absorbs a hydraulic shock generated in the secondary oil chamber.   The booster according to claim 5, wherein the secondary piston and the pressure regulating mechanism are arranged in parallel.   The booster according to claim 5 or 6, wherein the secondary piston is arranged around the center, and the ring-shaped pressure regulating mechanism is arranged on an outer peripheral portion of the secondary piston.   The booster according to claim 5 or 6, wherein the pressure regulating mechanism is arranged at the center, and the ring-shaped secondary piston is arranged on an outer peripheral portion of the pressure regulating mechanism.   The booster according to any one of claims 5 to 8, wherein the communication path is provided in the pressure regulating mechanism.

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