JPH10338154A - Hydraulic pump for automobile - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize shift corresponding to the operating state of a hydraulic operating device to be supplied with oil pressure and shift corresponding to rotating speed of an engine to be a drive source, with simple constitution without using a sensor for detecting a travel state and a control means corresponding to the detected result of the sensor. SOLUTION: A hydraulic pump for an automobile is provided with a rotor 10 rotated by power transmitted from an input shaft 3 inter lockingly connected to the output end of an engine, and generates oil pressure supplied to a hydraulic operating device mounted on the automobile. In this case, a speed change means 5 and a hydraulic clutch 6 are provided between the input shaft 3 and a rotor shaft 2 to be the rotating shaft of the rotor 10. The speed change means 5 switches a change gear ratio between both shafts 2, 3 to high or low, and the hydraulic clutch 6 puts the speed change means 5 in switching action by the action of oil pressure generated on the discharge side of a pump body 1 and supplied to the hydraulic operating device.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic pump for an automobile driven by an engine to generate a supply hydraulic pressure to a hydraulic actuator mounted on the automobile.

[0002]

2. Description of the Related Art Recent automobiles are equipped with various devices that are operated by hydraulic pressure, such as a power steering device and an automatic transmission, and are equipped with a hydraulic pump that generates hydraulic pressure to be supplied to these devices.

[0003] Many of such automotive hydraulic pumps include:
Utilizing a part of the power generated by the on-vehicle engine, for example, it is driven by belt transmission via a power take-off pulley provided at the end of the crankshaft of the engine. In the case of high speed running with a high engine rotation speed, there is a disadvantage that the power loss for driving the hydraulic pump is large and the fuel consumption is reduced, and the specifications of the hydraulic pump were determined to reduce this power loss. In such a case, there is a problem that the hydraulic pump is insufficient in capacity when the vehicle is running at a low speed or at a low speed when the rotation speed of the engine is low, and sufficient operating oil pressure cannot be obtained.

As described above, in a vehicle hydraulic pump used to generate a supply hydraulic pressure to a hydraulic operating device mounted on a vehicle, a sufficient operating hydraulic pressure is secured when necessary, and the engine serving as a drive source is inactive. In order to meet this demand, the following two configurations have been disclosed.

[0005] The first configuration is, for example, a hydraulic power steering device that assists the force required for steering by hydraulic pressure.
Many hydraulic actuators installed in automobiles, such as the need to supply hydraulic pressure only at the time of steering, pay attention to the fact that supply of operating hydraulic pressure is not always required.
As disclosed in Japanese Patent Application Publication No.
A pair of hydraulic pumps for supplying the operating hydraulic pressure is provided, and a clutch is interposed in the middle of the transmission system to one of the hydraulic pumps, and the clutch is used as a detection result of a running state such as an engine speed, a steering state, and the like. In this case, one hydraulic pump is driven when necessary, and two hydraulic pumps are driven only when necessary.

[0006] In this configuration, one of the hydraulic pumps is constantly driven because the flow of the hydraulic oil is constantly generated to prevent the hydraulic oil from becoming viscous at a time when the outside air temperature is low. The power loss can be reduced as much as possible by using a small-capacity hydraulic pump that is constantly driven.

A second configuration is a ring cone type continuously variable transmission between an input shaft interlocked with an engine and a rotor shaft of a hydraulic pump, as disclosed in Japanese Patent Application Laid-Open No. 7-133854. The transmission ring of this continuously variable transmission is pressed and moved by a pressing body that moves in the radial direction by the action of centrifugal force according to the rotation of the input shaft to change the gear ratio. By transmitting this rotation to the hydraulic pump as it is and transmitting it to the hydraulic pump after a predetermined deceleration during high-speed rotation of the engine, power loss during high-speed running can be reduced and hydraulic oil shortage at low-speed running can be eliminated. It is intended to be realized at the same time.

As the continuously variable transmission disposed between the input shaft and the rotor shaft, another type of continuously variable transmission such as a variable pitch pulley type is used instead of the above-described ring cone type continuously variable transmission. The change of the gear ratio can be realized by using an appropriate actuator that operates according to the detection result of the running state of the vehicle, such as the rotation speed of the engine, the state of steering, and the like. Hydraulic pumps have also been proposed.

[0009]

However, the first configuration requires two hydraulic pumps, a transmission system for each of these hydraulic pumps and the engine, and a clutch interposed in one of the transmission systems. A sensor for detecting a running state,
A control device that controls the engagement and disengagement of the clutch based on the detection result of the sensor is required, which complicates the overall configuration and may cause a malfunction due to the influence of external noise.

On the other hand, in the second configuration, since the gear ratio between the input shaft and the rotor shaft is changed by mechanical means due to the action of centrifugal force, there is a risk of malfunction due to the influence of external noise. Although there is no advantage, there is a problem that it is difficult to reduce the size of the continuously variable transmission including the transmission means,
When using a continuously variable transmission of another type instead of a ring cone type continuously variable transmission to reduce the size, a large amount of force is required to change the gear ratio, and the centrifugal force causes There is a problem that it is difficult to realize a mechanical transmission means.

Further, in this configuration, the gear ratio is changed only in accordance with the level of the engine speed, and the operating state of the hydraulic operating device to which the operating hydraulic pressure is supplied is not reflected. There is a problem that the engine is forced to lose unnecessary power in a running state in which supply is not required.

As described above, this problem can be solved by using an appropriate actuator that operates according to the result of detection of the running state of the vehicle for realizing the gear shift. Although it can be realized using a continuously variable transmission of a type other than the cone type, in this case, as in the first configuration, a sensor for detecting the traveling state and a detection result of the sensor are used. A control device for controlling the actuator is required, which leads to a complicated overall configuration and a possibility of malfunction due to the influence of external noise.

The present invention has been made in view of the above circumstances, and detects a running state of a shift corresponding to an operating state of a hydraulic operating device and a shift corresponding to a rotational speed of an engine serving as a driving source. Sensors and control means according to the detection result are not required, and can be realized by mechanical means. Unnecessary power loss of the engine as a drive source while securing sufficient supply hydraulic pressure only when necessary It is an object of the present invention to provide an automotive hydraulic pump capable of reducing as much as possible.

[0014]

SUMMARY OF THE INVENTION An automotive hydraulic pump according to the present invention includes a rotor that rotates by transmission from an input shaft that is operatively connected to an output end of an engine. In an automotive hydraulic pump for generating supply hydraulic pressure, a transmission means disposed between the input shaft and the rotor, for switching a speed ratio between the two to a high or low value, And a hydraulic clutch for performing a switching operation.

The present invention utilizes the fact that the hydraulic pressure generated by a hydraulic pump for a vehicle changes according to the operating state of a hydraulic operating device to which it is supplied, and increases during operation and decreases during non-operation. I do. During the operation of the hydraulic operating device that requires a hydraulic supply, the hydraulic clutch operates by the action of the supply hydraulic pressure that rises with this, and the speed change means disposed between the input shaft from the engine and the rotary shaft of the rotor operates. Switch to high speed side,
The rotation speed of the rotor increases to secure a sufficient supply oil pressure.
Also, during the non-operation of the hydraulic actuator that does not require hydraulic supply,
The hydraulic clutch is operated by the action of the supplied hydraulic pressure that is reduced in accordance with this, the speed change means is switched to a low speed side, the rotation speed of the rotor is reduced, and the power loss of the engine as the drive source is reduced.

In addition, a centrifugal spool is provided which moves by the action of centrifugal force accompanying the rotation of the input shaft, releases the pressure applied to the hydraulic clutch, and inhibits the shifting operation of the speed change means to a high speed side. And

In the present invention, when the rotation of the input shaft interlocked with the output end of the engine becomes excessive, the centrifugal spool moves by the action of the centrifugal force accompanying this rotation.
The switching operation of the transmission means to the high-speed side is prohibited, so that the rotation speed of the rotor is not excessively increased, and the power loss of the engine serving as the driving source is reduced. At this time, the rotation speed of the input shaft is transmitted to the rotor at a reduced speed by the speed change means. However, since the rotation speed of the input shaft itself is high, the rotation speed of the rotor is maintained at a somewhat high level, and the rotation to the hydraulic actuator is controlled. The supply hydraulic pressure is sufficiently secured.

The operating pressure release oil passage is provided with a variable throttle that changes a throttle area by a control edge formed in a part of the centrifugal spool, and a predetermined throttle resistance is added to the pressure oil that has passed through the variable throttle. A fixed aperture.

According to the present invention, when the centrifugal spool moves in response to the increase in the rotation speed of the input shaft, the operating pressure on the hydraulic clutch passes through the variable throttle that changes the throttle area by the control edge formed on the centrifugal spool. Then, it is released through the fixed aperture. As a result, the abrupt change in the working pressure is reduced, and the switching operation of the hydraulic clutch is not performed abruptly, so that the discontinuity of the pressure characteristic on the discharge side of the hydraulic pump is eliminated and a smooth pressure characteristic is obtained. This variation can be easily adjusted by additional processing of the control edge and the fixed aperture, and a desired pressure characteristic can be obtained.

Further, the speed change means is coaxially arranged between the rotating shaft and the input shaft, and a planetary body held by a carriage that rotates integrally with the rotating shaft of the rotor. A sun disk that is in contact with each other from the inside, and a one-way clutch that is interposed between the sun disk and the input shaft, and that allows a preceding rotation of the sun disk, wherein the hydraulic clutch is A clutch plate that rotates integrally with the carriage,
A piston that is restricted in rotation by the input shaft, moves in the axial direction by the action of the supply hydraulic pressure, and is pressed against the clutch plate.

In the present invention, the speed change means between the input shaft and the rotor includes the planetary body and the sun disk,
Normally, as a planetary roller transmission or a planetary gear transmission, the rotation of the input shaft is transmitted to the rotation shaft of the rotor by reducing the rotation of the input shaft via the sun disk, the planetary bodies and these carriages, or between the input shaft and the rotor. To be compact. Switching of the speed change means to a high speed side includes a clutch plate which rotates integrally with the carriage, a piston which is restricted in rotation by an input shaft, moves in the axial direction by the action of supply hydraulic pressure, and is pressed against the clutch plate. This is realized by the operation of a hydraulic clutch that is compactly formed on one side of the transmission means, by constraining the rotating shaft of the rotor via a carriage that rotates integrally with the clutch plate and rotating the rotor at the same speed as the input shaft. Note that a preceding rotation that occurs with respect to the input shaft on the solar disk that is in rolling contact with the planetary body due to the restraint of the carriage is allowed by a one-way clutch interposed between the solar disk and the input shaft.

[0022]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the drawings showing the embodiments. FIG. 1 is a longitudinal sectional view showing a first embodiment of an automotive hydraulic pump according to the present invention.

The illustrated hydraulic pump for an automobile is a pump body configured as a vane pump having a short cylindrical rotor 10 having a plurality of vanes movably in a radial direction and a cam ring 11 having an uneven annular shape. 1 is provided. The cam ring 11 is housed inside the pump housing 14 together with the pressure plate 12 coaxially positioned on one side thereof, and is located between the end plate 13 closing the other side of the pump housing 14 and the pressure plate 12. It is clamped and fixed.

The rotor 10 penetrates through the axial centers of the pressure plate 12 and the cam ring 11, and is spline-coupled to an intermediate portion of the rotor shaft 2, the tip of which is supported by the end plate 13. Cam ring sandwiched between pressure plate 12 and end plate 13 as a shaft
It is designed to rotate inside 11.

A plurality of recesses are provided in the circumferential direction inside the cam ring 11, and a pump chamber is formed between these recesses and the outer peripheral surface of the rotor 10. The plurality of vanes held by the rotor 10 are urged radially outward by the action of hydraulic pressure generated in the pressure chamber 17, and are pressed against the inner peripheral surface of the cam ring 11, including the inside of each pump chamber. The rotation of the rotor 10 accompanying the rotation of the rotor shaft 2 is performed while maintaining the pressed state of each vane.

Each of the pump chambers includes a pump housing
The suction oil passage 16 formed in the peripheral wall of 14 and the end plate 13
Through a pressure chamber 17 formed on the back side of the pressure plate 12, and a discharge chamber 18 formed in the pump housing 14. The discharge pipe is connected to an appropriate hydraulic actuating device, such as a power steering device, to which hydraulic pressure is supplied, and the suction pipe 15 is
Each is connected to an oil tank for storing hydraulic oil of a hydraulic actuator.

With the rotation of the rotor shaft 2, the rotor
When 10 rotates, hydraulic oil is introduced into each of the pump chambers arranged on the outside of the rotor 10 through the suction pipe 15 and the suction oil passage 16, and the introduced oil flows between adjacent vanes. The pressure is increased while being rotated together with the rotor 10 and discharged to the discharge pipe through the pressure chamber 17 and the discharge chamber 18 and supplied to an appropriate hydraulic actuator.

The rotor shaft 2, which is the rotation shaft of the rotor 10, penetrates the pump housing 14 on the side of the pressure chamber 17 and projects to an appropriate length outside. A transmission housing 19 is coaxially attached to the end of the pump housing 14 on the same side,
An input shaft 3 is rotatably supported on the transmission housing 19 coaxially with the front rotor shaft 2. One end of the input shaft 3 is projected out of the transmission housing 19 by an appropriate length, and is not shown via a V-pulley 30 fitted and fixed to the protruding end and a V-belt wound around the V-pulley 30. It is connected to the output end of the engine.

The input shaft 3 extended in the transmission housing 19
Of the rotor shaft 2 protruding from the pump housing 14 is abutted on the other end thereof.
A transmission chamber 4 having a circular cross section is formed coaxially, and inside the transmission chamber 4 is formed a transmission means 5 and a hydraulic clutch 6 which are features of the present invention.

The illustrated speed change means 5 is configured as a planetary roller transmission having a sun roller 50, a planetary roller 51 and a fixed ring 52. The sun roller 50 is a disk having an appropriate thickness, and is interposed between the butting ends of the rotor shaft 2 and the input shaft 3, and has support shafts projecting to both sides in the thickness direction. And is coaxially supported with them.

The support of the sun roller 50 on the rotor shaft 2 side is as follows.
With the bush fitted and fixed to the shaft center of the rotor shaft 2,
It is made relatively rotatable. On the other hand, a one-way clutch 20 that allows the sun roller 50 to rotate in advance is interposed in the support portion of the sun roller 50 on the input shaft 3 side. As a result, the sun roller 50 rotates in accordance with the rotation of the input shaft 3 due to the engagement of the one-way clutch 20 in the normal state where the rotation of the input shaft 3 precedes, while the rotation of the sun roller 50 is controlled by the rotation of the input shaft 3 as described later.
When the one-way clutch 20 is disengaged, the one-way clutch 20 can be freely idled between the rotor shaft 2 and the input shaft 3 without being restricted by the two. it can.

The fixing ring 52 is fitted and fixed inside the transmission chamber 4 at a position substantially aligned with the position of the sun roller 50 in the axial direction.
Are arranged substantially equally in the circumferential direction. These planetary rollers 51, 51…
Are rotatably mounted on respective support shafts protruding from one surface of a disk-shaped carriage 53 coaxially spline-coupled to the end of the rotor shaft 2, and the outer peripheral surface of the sun roller 50 and a fixing ring
The carriage 53 is rotated in contact with the inner peripheral surface of the carriage 52 so as to rotate around each of the support shafts by the rolling of the carriage 53.
At the same time, it revolves around the axis of the rotor shaft 2.

When the input shaft 3 is driven to rotate by transmission from an engine (not shown), the rotation is transmitted to the sun roller 50 via the one-way clutch 20, and the sun roller 50 rotates around the axis. Are rotated, and the planetary rollers 51, 51,..., Which are in contact with the outer circumference thereof, rotate, and these carriages 53 revolve. At this revolving speed, the rotor shaft 2 and the rotor 10 are rotationally driven. At this time, the rotation of the input shaft 3 is transmitted to the rotor shaft 2 at a reduced speed, and the rotor shaft 2 and the rotor 10 are driven at a lower speed than the rotation speed of the input shaft 3.

On the other hand, a disc-shaped clutch plate 60 is integrally attached to the tip of the support shaft of each of the planetary rollers 51, 51,... Protruding from the carriage 53. The hydraulic clutch 6 is constituted by the clutch piston 61 disposed opposite to the clutch piston 61.

The clutch piston 61 has its inner diameter side engaged with a spline formed on the outer periphery of the input shaft 3 in the middle part.
The input shaft 3 is rotatably restrained, and is mounted so as to be movable in the axial direction. A coil is provided between the input shaft 3 and a spring receiver 62 which is fixed to the tip of the input shaft 3 on the side facing the clutch plate 60. With the spring 63 interposed, the spring force of the coil spring 63 allows
It is urged in a direction away from the clutch plate 60.

The clutch piston thus mounted
61 includes a small-diameter portion 61a protruding coaxially on the non-opposite side of the clutch plate 60, and the outer diameter side of the clutch piston 61 is provided in the inner cavity of the transmission housing 19 constituting the transmission chamber 4, and The small diameter portion 61a is fitted into a fitting hole provided continuously on the same side of the transmission chamber 4 through separate seal rings 64 and 65, and the small diameter portion 61a is Seal ring 6
A cylinder chamber 66 whose both sides are liquid-tightly sealed is formed by the cylinders 4 and 65.

The cylinder chamber 66 is communicated with the discharge chamber 18 of the pump body 1 by an oil guide passage 67 formed in the transmission housing 19 and the pump housing 14.
The other side is a return oil passage 68 formed in the pump housing 14.
Thereby, it communicates with the suction oil passage 16 of the pump body 1.
Thereby, the hydraulic pressure generated in the discharge chamber 18 by the rotation of the rotor 10 inside the pump body 1 and supplied to the hydraulic operating device (not shown) is introduced into the cylinder chamber 66 through the oil guide path 67. On the other hand, at this time, the other side of the clutch piston 61
Since the low pressure state is maintained by the communication with the suction oil passage 16, the clutch piston 61 is pressed toward the clutch plate 60 by the action of the hydraulic pressure supplied to the hydraulic operating device. , And moves toward the clutch plate 60 and is pressed against the clutch plate 60.

FIG. 2 is an explanatory view of the operation of the hydraulic clutch 6, showing a state in which the clutch piston 61 is pressed against the clutch plate 60 by the action of the above-described supply hydraulic pressure introduced into the cylinder chamber 66. In such a state, the clutch plate 60 rotates at the same speed as the clutch piston 61 whose rotation is restricted by the input shaft 3, and the clutch plate 60 is supported by the planetary rollers 51, 51. Since the planetary rollers 51, 51,.
The carriage 53 and the rotor shaft 2 holding the carriage 53 rotate at the same speed as the input shaft 3. On the other hand, at this time, the sun roller 50 rotates at a high speed in accordance with the rolling of the planetary rollers 51, 51... On the outer peripheral surface thereof. This is permitted by the direction clutch 20 and does not hinder the rotation of the input shaft 3 and the rotor shaft 2.

As described above, the hydraulic clutch 6 is provided in the cylinder chamber.
By the action of the hydraulic pressure introduced into the transmission 66, an operation of switching the transmission ratio of the transmission means 5 configured as a planetary roller transmission to a high or low state is performed. This switching occurs on the discharge side by the operation of the pump body 1 and is performed according to the level of the hydraulic pressure introduced into the cylinder chamber 66.

The hydraulic pressure generated on the discharge side of the pump body 1 is
It changes according to the operation state of the hydraulic operating device to which this is supplied.For example, in a hydraulic power steering device that assists the force required for steering of an automobile by hydraulic pressure, the supply hydraulic pressure to the device is Ascends with steering. When the hydraulic pump for an automobile according to the present invention is used, the clutch piston 61 moves and is pressed against the clutch plate 60 by the action of the supply hydraulic pressure which rises as described above, and the transmission means 5 is switched to the high-speed side. As a result, the rotation speed of the rotor shaft 2 and the rotor 10 increases, and the generated oil pressure on the discharge side of the pump body 1 further increases, so that the operation of the hydraulic actuator by the supply of this oil pressure can be performed reliably.

On the other hand, when the hydraulic pressure supplied to the power steering device is reduced due to the stop of the steering, the clutch piston 61 is pressed in the opposite direction by the spring force of the coil spring 63, and as shown in FIG. Depart from. At this time, the rotation of the input shaft 3 is transmitted to the rotor shaft 2 and the rotor 10 through the deceleration by the transmission means 5 as described above, and as a result of the rotor 10 rotating at a low speed, the power loss of the engine serving as the driving source is greatly reduced. can do.

Further, as shown in FIG.
In 61, a through-hole 70 is formed, which has one end opened inside the cylinder chamber 66 and penetrates in the axial direction, and a spool chamber 71 communicating with a middle portion of the through-hole 70 extends radially from the outer peripheral surface. The spool chamber is formed as a drilled circular hole.
The centrifugal spool 7 is stored in 71.

FIG. 3 is an enlarged sectional view near the spool chamber 71 for explaining the operation of the centrifugal spool 7. As shown, the centrifugal spool 7 is housed inside the spool chamber 71 so as to be slidable in the depth direction, that is, movably in the radial direction of the clutch piston 61. Clutch piston
The open end of the spool chamber 71 to the outer diameter side of the cylinder 61 is sealed in a liquid-tight manner by a lid member 72 screwed thereto, and the centrifugal spool 7 is interposed between the spool member 71 and the lid member 72. Coil spring 73
The spring force of the clutch piston 61 urges the inner side of the spool chamber 71, that is, the clutch piston 61 radially inward.

A spool chamber 71 for storing the centrifugal spool 7
Is a communication hole 74 formed radially inward from the bottom thereof.
As a result, the clutch piston 61 communicates with the inner peripheral side of the clutch piston 61, and is maintained at substantially the same pressure as the chamber in which the transmission means 5 is disposed. The centrifugal spool 7 is formed with a communication hole 75 penetrating the axial center thereof, and communicates with the space on both sides of the centrifugal spool 7 inside the spool chamber 71. Sliding occurs such that it is not affected by the pressure difference across it.

As described above, the centrifugal force acts on the centrifugal spool 7 held by the clutch piston 61 in accordance with the rotation of the clutch piston 61 accompanying the rotation of the input shaft 3 as shown by the white arrow in the drawing. The direction of action is the clutch piston
61, that is, in the direction opposite to the direction of action of the spring force of the coil spring 73, the centrifugal spool 7
Slides according to the balance between the centrifugal force and the spring force.

The rotation speed of the input shaft 3 is low and the centrifugal spool 7
When the centrifugal force acting on the spool is less than the spring force of the coil spring 73, the centrifugal spool 7 is restrained at a position in contact with the bottom of the spool chamber 71, and as shown in FIG. The above-mentioned through-hole 70 intersecting is closed.

On the other hand, when the rotation speed of the input shaft 3 is high and the centrifugal force acting on the centrifugal spool 7 exceeds the spring force of the coil spring 73, the centrifugal spool 7 slides outward in the radial direction. When the amount of movement exceeds a predetermined amount, as shown in FIG.
Is released, and the cylinder chamber 66 formed on one side of the clutch piston 61 is connected to the other side, that is, the transmission means 5 inside the transmission chamber 4.
Will be connected to the installation space.

FIG. 2 shows that the rotation speed of the input shaft 3 is low,
3 shows the operating state of the hydraulic clutch 6 when the centrifugal spool 7 is at the position shown in FIG. FIG. 4 is a diagram illustrating the operation of the hydraulic clutch 6 in a state where the rotation speed of the input shaft 3 is high and the centrifugal spool 7 is moved to the position shown in FIG. .

When the centrifugal spool 7 is at the position shown in FIG. 3B, the through-hole 70 is opened, and the space for disposing the speed change means 5 communicating with the cylinder chamber 66 by this opening is as described above. Thus, the return oil passage is connected to the suction oil passage 16 of the pump body 1.
When the sliding position of the centrifugal spool 7 is in the state shown in FIG.
The hydraulic pressure introduced into the 66 as described above is released to the space in which the transmission means 5 is disposed through the through hole 70, and is further returned to the suction oil passage 16 of the pump body 1 via the return oil passage 68. Accordingly, the internal pressure of the cylinder chamber 66 does not change irrespective of the supply oil pressure generated on the discharge side of the pump body 1, the clutch piston 61 does not move due to the action of the internal pressure, and moves toward the high speed side of the speed reduction means 5. As a result, the rotor shaft 2 and the rotor 10 are driven at a lower speed than the rotation speed of the input shaft 3.

As described above, when the rotation speed of the input shaft 3 driven by the engine becomes excessive, the centrifugal spool 7 moves by the action of the centrifugal force accompanying the rotation, and releases the operating pressure to the hydraulic clutch 6. Thus, the operation of prohibiting the switching of the speed change means 5 to the high speed side is performed.
The rotation speed of the rotor shaft 2 and the rotor 10 does not increase excessively with the increase in the rotation speed of the input shaft 3, and unnecessary power loss of the engine during high-speed rotation can be reduced. In this state, since the rotation speed of the input shaft 3 is high, the rotation speed of the rotor 10 driven through the deceleration by the speed reduction means 5 is sufficiently ensured, and the hydraulic operating device using the supply oil from the pump body 1 is provided. There is no danger that the operation of will be impaired.

In the above embodiment, the case where the pump body 1 is a vane pump has been described, but it goes without saying that other types of pump bodies 1 such as a gear pump and a trochoid pump may be provided.

As the transmission means 5, various types of transmissions capable of switching between high and low stages can be used. By using the planetary roller transmission or the planetary gear transmission shown in this embodiment, In addition, the pump body 1 can be made compact on one side including the hydraulic clutch 6 that performs the switching operation.

FIGS. 5 and 6 are enlarged sectional views of a main part of a second embodiment of the automotive hydraulic pump according to the present invention. These figures show the speed change means 5 and the hydraulic clutch 6 formed at the butting portion of the rotor shaft 2 and the input shaft 3 inside the pump housing 14 and the transmission housing 19 which are coaxially assembled. Components common to those in the first embodiment are denoted by the same reference numerals.

The transmission means 5 in this figure is configured as a planetary gear transmission having a sun gear 50a, planetary gears 51a, 51a,... And a fixed gear 52a. The sun gear 50a is a disk-shaped external gear in which teeth that can mesh with the planetary gear 51a are formed on the entire outer peripheral surface, and includes a short support shaft protruding from both sides of the shaft center. The rotor shaft 2 and the input shaft 3 are rotatably supported coaxially between the butting ends of the rotor shaft 2 and the input shaft 3.
As in the first embodiment, a one-way clutch 20 is interposed in the support portion of the sun gear 50a on the input shaft 3 side to allow the sun gear 50a to rotate in advance with respect to the input shaft 3. .

The fixed gear 52a is a ring-shaped internal gear having teeth that can mesh with the planetary gear 51a all around the inner peripheral surface, and is substantially aligned in the axial direction with the arrangement position of the sun gear 50a. To fit inside the pump housing 14. The planetary gears 51a, 51a,... Are rotatably mounted on one surface of a disk-shaped carriage 53 which rotates together with the rotor shaft 2 by separate support shafts.
52a is meshed with the inner teeth.

When the input shaft 3 rotates with the above configuration,
This rotation is transmitted to the sun gear 50a via the one-way clutch 20, and in accordance with the rotation of the sun gear 50a, the planetary gears 51a, 51a,.
., The carriage 53 of the planetary gears 51a, 51a,... Revolves, and the rotor shaft 2 and the rotor 10 are driven to rotate at this revolution speed. At this time, the rotation speeds of the rotor shaft 2 and the rotor 10 are sufficiently lower than the rotation speed of the input shaft 3.

The hydraulic clutch 6 includes planetary gears 51a, 51a
The clutch plate 60, which is supported collectively on the distal end of the support shaft and rotates integrally with the carriage 53 and the rotor shaft 2, is restrained from rotating by the input shaft 3 so as to face the clutch plate 60, and has a shaft length direction. Movably mounted clutch piston 61
It is comprised including. The clutch piston 61 is urged in a direction away from the clutch plate 60 by a leaf spring 63a interposed between the clutch piston 61 and a spring receiver 62 fixed to the input shaft 3.

The clutch piston thus mounted
61 is provided coaxially on the non-opposite side of the clutch plate 60,
The transmission housing 19 is provided with a small diameter portion 61a fitted through a seal ring 64 in a fitting hole provided continuously on the same side of the transmission housing 19, and a fitting portion between the small diameter portion 61a and the input shaft 3 has a seal ring. 65
Is interposed. Thus, a liquid-tightly sealed cylinder chamber is provided between the oil seal 8 for sealing the protruding portion of the input shaft 3 from the transmission housing 19 and the end face of the small diameter portion 61a.
66 is formed.

As in the first embodiment, the cylinder chamber 66 is communicated with the discharge side of a pump body (not shown) by an oil guide passage 67 formed in the transmission housing 19 and the pump housing 14. The hydraulic pressure generated inside the pump main body according to the rotation of the shaft 2 and supplied to a hydraulic actuator (not shown) is introduced. The pump body may be the vane pump shown in FIG. 1, or may be another type of pump such as a gear pump or a trochoid pump.

On the other side of the clutch piston 61, a clutch plate 61b in the form of a hollow disk is attached so as to face the outer peripheral side of the clutch plate 60.
When the clutch piston 61 moves against the bias of 3a,
It comes into sliding contact with the clutch plate 60. As described above, since the clutch plate 61b is formed separately from the clutch piston 61, the material of the clutch plate 61b can be freely selected, and the degree of friction accompanying sliding contact with the clutch plate 60 is appropriately set. It is possible to do.

An installation chamber of the speed reduction means 5 to which the other side of the clutch piston 61 faces is communicated with a suction side of a pump body (not shown) by a fixed throttle 68a formed as a small-diameter hole penetrating the end wall of the pump housing 14. And maintained at low pressure. As a result, the clutch piston 61 is pressed toward the clutch plate 60 by the action of the hydraulic pressure introduced into the cylinder chamber 66, and this pressing force exceeds the spring force of the leaf spring 63a and moves toward the clutch plate 60. As shown in 5,
It is pressed against the clutch plate 60 via the clutch plate 61b.

At this time, the carriage 53 of the planet gears 51a, 51a,... To which the clutch plate 60 is attached rotates at the same speed as the clutch piston 61 whose rotation is restricted by the input shaft 3. Rotor shaft 2 for supporting
Rotates at the same speed as the input shaft 3. Then sun gear
50a rotates at a high speed in accordance with the rotation of the planetary gears 51a, 51a,... Meshing with the external teeth, but this rotation is permitted by the one-way clutch 20 interposed between the input shaft 3 and the input shaft. It does not hinder the integral rotation of the shaft 3 and the rotor shaft 2.

As described above, the hydraulic clutch 6 is provided in the cylinder chamber.
By the action of the internal pressure 66, an operation of switching the speed ratio of the speed change means 5 configured as a planetary gear transmission to a high or low state is performed. As in the first embodiment, the internal pressure of the cylinder chamber 66 changes according to the operating state of the hydraulic operating device serving as the delivery destination of the discharge pressure of the pump body, and is high during operation and high during non-operation. Will be lower. Therefore, switching of the speed change means 5 to the high-speed side is performed only during the operation of the hydraulic operating device. During this operation, the rotor shaft 2 rotates at a high speed, so that a sufficient amount of high-pressure hydraulic oil is supplied. By the feeding, the operation of the hydraulic operating device can be reliably performed. On the other hand, when the hydraulic operating device is not operating, the rotor shaft 2 rotates at a low speed.
The power burden on the engine serving as the driving source can be greatly reduced.

A spool chamber 71 is formed in the clutch piston 61 performing the above operation as a circular hole penetrating in the radial direction from the outer peripheral surface. The spool chamber 71 accommodates the centrifugal spool 7a. Also, the clutch piston 61 has
First throttle hole 7 that connects spool chamber 71 to cylinder chamber 66
0a and a second throttle hole 70b communicating with the disposition chamber of the speed change means 5 on the outside in the radial direction are formed in the axial direction.

FIG. 7 is an enlarged sectional view near the spool chamber 71 for explaining the operation of the centrifugal spool 7a. As shown in the drawing, the spool chamber 71 has an open end on the outer diameter side of the clutch piston 61 liquid-tightly sealed by a lid member 72 screwed thereto, and the open end on the other side is closed by the outer periphery of the input shaft 3. It is composed of The centrifugal spool 7a is provided with two land portions slidably fitted in the spool chamber 71 on both sides in the axial direction, and these are connected by a small diameter portion.
The spring is biased toward the inside of the spool chamber 71 by a spring force of a coil spring 73 interposed between the clutch piston 72 and the clutch spring 61 so that the clutch piston 61 can move in the radial direction against the bias. .

The lands on both sides of the centrifugal spool 7a are arranged such that the distance between their opposing surfaces is the first and second lands in the spool chamber 71.
The control edges 71a and 71b are formed by chamfering the entire periphery of the opposing edge of each land portion. Also, both sides of the centrifugal spool 7a inside the spool chamber 71 are substantially communicated with the side where the transmission means 5 is disposed, respectively, by a communication hole 74a penetrating through the axial center portion of the lid member 72 and a fitting gap between the input shaft 3 and the communication hole 74a. The pressure is kept constant, and the movement of the centrifugal spool 7a in the spool chamber 71 occurs without being affected by the pressure difference on both sides.

As described above, the centrifugal spool 7a housed in the spool chamber 71 is provided with a hollow arrow in the drawing according to the rotation of the clutch piston 61 accompanying the rotation of the input shaft 3.
A centrifugal force acts radially outward, that is, in a direction opposite to the direction of action of the spring force of the coil spring 73, and the centrifugal spool 7a
Slides according to the balance between the centrifugal force and the spring force.

The rotation speed of the input shaft 3 is low and the centrifugal spool
When the centrifugal force acting on 7a is lower than the spring force of the coil spring 73, the centrifugal spool 7a comes into contact with the outer peripheral surface of the input shaft 3, which is the bottom surface of the spool chamber 71, as shown in FIG. It is in the position that was. At this time, the first throttle hole 70a opens between the land portions on both sides of the centrifugal spool 7a, and the second throttle hole 70b opens outside the outer land portion.
Internal pressure stops inside the spool chamber 71. At this time, the transmission means 5 is switched by the operation of the hydraulic clutch 6 as described above, and the rotation speed of the rotor shaft 2 changes to a high level or a low level.

On the other hand, when the rotation speed of the input shaft 3 is high and the centrifugal force acting on the centrifugal spool 7a exceeds the spring force of the coil spring 73, the centrifugal spool 7a slides outward in the radial direction, and the sliding amount is reduced. When the predetermined amount is reached, as shown in FIG.
The second throttle hole 70b opens inside the outer land portion, and the cylinder chamber 66 communicates with the space in which the speed change means 5 is provided. Thereby, the internal pressure of the cylinder chamber 66 is reduced to the first and second throttle holes 70.
The air is released to the disposition chamber of the transmission means 5 through a and 70b, and further released to the suction side of the pump body through the fixed throttle 68a as shown in FIG.

Accordingly, the internal pressure of the cylinder chamber 66 is kept lower than the hydraulic pressure generated on the discharge side of the pump body, and the movement of the clutch piston 61 does not occur due to the action of this internal pressure. As a result, the rotor shaft 2 is driven at a lower speed than the rotation speed of the input shaft 3.

As described above, similarly to the centrifugal spool 7 in the first embodiment, when the rotation speed of the input shaft 3 exceeds a predetermined amount, the centrifugal spool 7a releases the pressure applied to the hydraulic clutch 6 to change the speed. The switching of the means 5 to the high-speed side is prohibited, and the function of reducing unnecessary power loss of the engine during high-speed running is achieved.

Further, in the second embodiment, the release of the working pressure in accordance with the movement of the centrifugal spool 7a is performed via a release oil passage having first and second throttle holes 70a and 70b and a fixed throttle 68a. The configuration is performed. Thereby, the release of the working pressure is achieved by the first and second throttle holes 70a, 7 as variable throttles.
0b and the fixed throttle 68a occur slowly with the flow resistance when the pressure oil flows through it, the switching operation of the hydraulic clutch 6 is not performed rapidly, and the pressure characteristic on the discharge side of the hydraulic pump is discontinuous. And smooth pressure characteristics can be obtained. Further, the manner of changing the drawing area in the first and second drawing holes 70a and 70b can be freely changed by changing the shape of the control edges 71a and 71b formed as described above on the land portion of the centrifugal spool 7a. The timing of the switching operation and the operation speed can be adjusted, and desired pressure characteristics can be easily achieved.

[0073]

As described above in detail, in the hydraulic pump for an automobile according to the present invention, between the input shaft and the rotor operatively connected to the output end of the engine, the speed change means for switching the speed ratio between the two to high and low. And a hydraulic clutch for performing the switching operation of the transmission means by the action of the supply hydraulic pressure generated by the rotation of the rotor. This can be performed without the need for a sensor for detection and control means according to the detection result, and when the hydraulic operating device that does not need hydraulic pressure supply is not operating, the rotation speed of the rotor decreases and the The power loss can be reduced, and the rotation speed of the rotor can be increased during operation of the hydraulic operating device to ensure a sufficient supply hydraulic pressure.

Further, since the centrifugal spool which moves by the action of the centrifugal force accompanying the rotation of the input shaft and releases the working pressure to the hydraulic clutch is provided, the speed change according to the rotation speed of the engine as the driving source can be performed at the rotation speed. This is realized without the need for a sensor for detection and control means in accordance with the detection result. When the engine is rotating at high speed, the shift means is not switched to the high speed side, and the engine speed is increased due to excessive increase in the rotation speed of the rotor. Unnecessary power loss can be further reduced.

Further, since a variable throttle and a fixed throttle are provided in the oil passage for releasing the operating pressure to the hydraulic clutch, the change in the operating pressure to the hydraulic clutch due to the movement of the centrifugal spool becomes gentle, and the switching operation of the hydraulic clutch is performed. It is not performed suddenly, eliminating discontinuities in pressure characteristics on the discharge side of the hydraulic pump.
This pressure characteristic can be easily adjusted by processing the control edge and the fixed throttle provided on the centrifugal spool, and a desired pressure characteristic can be obtained.

Further, since the speed change means is constituted by a planetary type transmission, it can be formed compactly on one side of the pump main body together with the hydraulic clutch for changing the speed ratio, and the above-mentioned effects are realized by the large size of the entire structure. The present invention has an excellent effect, for example, it can be realized without inducing.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a first embodiment of an automotive hydraulic pump according to the present invention.

FIG. 2 is an explanatory diagram of an operation of a hydraulic clutch.

FIG. 3 is an enlarged sectional view near the spool chamber for explaining the operation of the centrifugal spool.

FIG. 4 is a diagram illustrating the operation of the hydraulic clutch when the centrifugal spool moves.

FIG. 5 is an enlarged sectional view of a main part of a second embodiment of the automotive hydraulic pump according to the present invention.

FIG. 6 is an essential part enlarged sectional view showing a second embodiment of the automotive hydraulic pump according to the present invention.

FIG. 7 is an enlarged sectional view near the spool chamber for explaining the operation of the centrifugal spool in the second embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Pump main body 2 Rotor shaft 3 Input shaft 5 Transmission means 6 Hydraulic clutch 7 Centrifugal spool 7a Centrifugal spool 10 Rotor 14 Pump housing 19 Transmission housing 20 One-way clutch 50 Sun roller 50a Sun gear 51 Planetary roller 51a Planetary gear 53 Carriage 60 Clutch plate 61 Clutch piston 63 Coil spring 63a Leaf spring 66 Cylinder chamber 67 Oil guide passage 68 Reflux oil passage 68a Fixed throttle 70 Through hole 70a First throttle hole 70b Second throttle hole 71 Spool chamber 71a Control edge 71b Control edge 73 Coil spring

Claims (4)

[Claims] 1. An automotive hydraulic pump, comprising: a rotor that rotates by transmission from an input shaft interlocked to an output end of an engine, and generates hydraulic pressure supplied to a hydraulic actuator mounted on the vehicle. And a rotor, which is arranged between the rotor and the rotor, and switches a speed ratio between the two to a high and low level, and a hydraulic clutch that causes the speed changing means to perform a switching operation by the action of the supplied oil pressure. And automotive hydraulic pumps. And moving by the action of centrifugal force accompanying the rotation of the input shaft, releasing the operating pressure on the hydraulic clutch,
2. The hydraulic pump for an automobile according to claim 1, further comprising a centrifugal spool for inhibiting a shift operation of the speed change means to a high speed side. 3. A variable throttle for changing a throttle area by a control edge formed in a part of the centrifugal spool, and a predetermined throttle resistance is added to the pressure oil passing through the variable throttle. 3. The automotive hydraulic pump according to claim 1, further comprising: 4. The planetary body, wherein the speed change means is coaxially arranged between the rotation shaft and the input shaft, the planetary body being held by a carriage that rotates integrally with the rotation shaft of the rotor. Each having a one-way clutch that is interposed between the sun disk and the input shaft and that allows the sun disk to rotate in a forward direction. 4. The clutch according to claim 1, further comprising: a clutch plate that rotates integrally with the carriage; and a piston that is restricted in rotation by the input shaft, moves in an axial direction by the action of the supply hydraulic pressure, and is pressed against the clutch plate. An automotive hydraulic pump according to any of the preceding claims.