JP2002340052A - Hydraulic pump for automobile - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic pump for an automobile capable of securely changing slow and fast rotational speeds corresponding to an engine rotation speed by a simple constitution, and achieving compactness. SOLUTION: Between an input shaft 3 from an engine and a rotor shaft 2, a planetary speed increaser 4a to increase the rotational speed of the input shaft 3 to be transmitted to the rotor shaft 2, a centrifugal clutch 5a to directly couple the input shaft 3 and the rotor shaft 2 by action of centrifugal force in accordance with rotation of the input shaft 3, and a one-way clutch 6a provided to act to disconnect transmission by the planetary speed increaser 4a when the input shaft 3 is directly coupled with the rotor shaft 2 by connection of the centrifugal clutch 5a are provided. Inhibition of slow rotation of the rotor shaft 2 when directly coupled with the input shaft 3 is thus eliminated.

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 hydraulic pressure supplied to a hydraulic operating device mounted on the automobile.

[0002]

2. Description of the Related Art Recent automobiles are equipped with various devices operated by hydraulic pressure, such as a power steering device and an automatic transmission.
A hydraulic pump that generates hydraulic pressure supplied to these devices is mounted. Many of such automotive hydraulic pumps use a part of the power generated by an onboard engine, and are driven, for example, by belt transmission from a power take-off transmission pulley attached to a part of the output end of the engine. .

However, when such a simple power transmission structure is employed, there is a problem that the power loss for driving the hydraulic pump is large at the time of high-speed running with a high engine speed, leading to a reduction in fuel consumption. When the specifications of the hydraulic pump are determined so as to reduce the loss, there is a problem that the hydraulic pump lacks the capacity at the time of low-speed running or at a stop with a low engine speed, and a desired hydraulic pressure cannot be obtained.

To solve such a problem, Japanese Patent Application Laid-Open No. 5-45
No. 87, disposes a clutch and a motor between an engine and a hydraulic pump, controls the clutch based on the detection result of the vehicle speed, and drives the hydraulic pump by the motor during high-speed traveling. A motor vehicle hydraulic pump is disclosed in which a load on an engine is reduced and a hydraulic pump is driven by the engine and the motor to obtain a sufficient working oil pressure during low-speed running.

Japanese Patent Laid-Open Publication No. Sho 57-15064 discloses that two hydraulic pumps are used, and the number of operating units is switched according to the vehicle speed. There is disclosed a hydraulic pump for an automobile in which a power load is reduced and sufficient hydraulic pressure is obtained by driving two hydraulic pumps during high-speed running.

Further, in Japanese Patent Application Laid-Open No. Hei 7-133854, a transmission is arranged between an input shaft from an engine and a rotor of a hydraulic pump, and a transmission ratio of the transmission is determined by a centrifugal force applied to the input shaft. By changing the function, the hydraulic pump rotates at low speed during high-speed running to reduce the power load on the engine,
Also disclosed is an automotive hydraulic pump in which the hydraulic pump is rotated at a high speed during low-speed running to obtain a sufficient working oil pressure.

[0007]

SUMMARY OF THE INVENTION
In the configuration disclosed in Japanese Patent Application Laid-Open No. 5-4587, a motor for driving at high speed traveling is separately required.
In the configuration disclosed in Japanese Patent Application Laid-Open No. 57-15064, two hydraulic pumps themselves are required, which inevitably complicates the configuration, and realizes downsizing, which is an important issue when mounting on an automobile. There is a problem that is difficult.

In these configurations, a vehicle speed sensor for detecting a vehicle speed and a control unit for performing clutch engagement control or hydraulic pump on / off control based on the vehicle speed detected by the vehicle speed sensor are required. Inevitably, the configuration is complicated by these factors, and furthermore, there is a possibility that malfunction may occur due to the influence of electromagnetic noise in the engine room.

On the other hand, in the configuration disclosed in Japanese Patent Application Laid-Open No. Hei 7-133854, a gear shift is performed by a mechanical operation, so that occurrence of a malfunction due to the influence of electromagnetic noise is avoided. As a transmission disposed between the shaft and the rotor of the hydraulic pump, a continuously variable transmission capable of continuously changing the transmission ratio, such as a ring cone type transmission, is used. Also, there is a problem that the configuration of the transmission system including the speed changeover mechanism by the centrifugal force becomes complicated, and it is difficult to realize miniaturization.

The present invention has been made in view of such circumstances, and it is possible to surely realize the switching of the rotation speed in accordance with the level of the engine rotation speed with a simple configuration, and to reduce the size. It is an object to provide a hydraulic pump for automobiles.

[0011]

According to a first aspect of the present invention, there is provided a hydraulic pump for an automobile having an input shaft and a rotor which rotates by transmission from the input shaft, and is mounted on the automobile by rotation of the rotor. A hydraulic pump for an automobile that generates a supply hydraulic pressure to a hydraulic operating device, is disposed between a rotation shaft of the rotor and the input shaft, and increases the rotation of the input shaft to transmit the rotation to the rotation shaft. Speed increasing means, which is engaged by the action of centrifugal force accompanying the rotation of the input shaft, and a centrifugal clutch that directly connects the input shaft and the rotating shaft; and the input shaft and the rotating shaft are engaged by engagement of the centrifugal clutch. And a clutch that operates so as to cut off transmission by the speed increasing means when is directly connected.

According to a third aspect of the present invention, in the automobile hydraulic pump, the speed increasing means applies a reverse rotation torque when increasing the rotation of the input shaft and transmitting the rotation to the rotation shaft, thereby causing the rotation of the input shaft to rotate. A rotating member to which a rotation torque greater than the reverse rotation torque is applied when the shaft is directly connected, the clutch stops rotation of the rotation member when the reverse rotation torque is larger than the rotation torque; Is a one-way clutch that allows the rotation of the rotating member when is smaller than the rotating torque.

[0013] A vehicle hydraulic pump according to a fourth aspect of the present invention includes an input shaft, and a rotor that rotates by transmission from the input shaft. An automotive hydraulic pump for generating a supply hydraulic pressure, provided between a rotation shaft of the rotor and the input shaft, for increasing the rotation of the input shaft and transmitting the rotation to the rotation shaft; A centrifugal clutch arranged in parallel with the speed increasing means, engaged by the action of centrifugal force accompanying the rotation of the input shaft, and directly connecting the input shaft and the rotating shaft; and the input shaft or the rotating shaft and the speed increasing means. A one-way clutch that operates in response to a decrease in the speed of the rotating shaft due to engagement of the centrifugal clutch and interrupts transmission between the input shaft or the rotating shaft and the speed increasing means. And characterized in that:

In the first invention, the third invention and the fourth invention, when the vehicle is running at a low speed with a low engine speed or stopped,
The speed of the rotation of the input shaft from the engine is increased by speed increasing means and transmitted to the rotating shaft of the rotor, and the rotor is rotated at high speed to generate a desired hydraulic pressure. On the other hand, during high-speed running with a high engine speed, the centrifugal clutch is engaged by the action of centrifugal force due to the rotation of the input shaft, and the rotating shaft of the rotor is directly connected to the input shaft. To reduce the power loss of the engine for driving the hydraulic pump. Further, at this time, the transmission by the speed increasing means is interrupted by the one-way clutch in accordance with the decrease in the speed of the rotating shaft of the rotor due to the engagement of the centrifugal clutch, and the low-speed rotation of the rotor directly connected to the input shaft is hindered. Absent.

According to a second aspect of the present invention, in the vehicle hydraulic pump, the clutch is interposed between the speed increasing means and a stationary member provided near the speed increasing means. .

In the second invention, the low speed rotation of the rotary shaft of the rotor directly connected to the input shaft by the engagement of the centrifugal clutch reduces the slippage of the compactly disposed clutch between the speed increasing means and the stationary member. Tolerate.

According to a fifth aspect of the present invention, in the vehicle hydraulic pump, the speed-increasing means includes a sun wheel integrally rotating with the rotary shaft, and a sun wheel supported by the input shaft via a planet carrier to engage with the sun wheel. The planetary gearbox comprises a planetary gear having a planetary gear that revolves around the planetary gear and guide wheels for guiding the planetary gear to revolve.

In the fifth invention, the speed increasing means is a planetary speed increasing device such as a planetary gear speed increasing device or a planetary roller speed increasing device, and is compactly formed outside the rotary shaft and the input shaft.

Further, the rotating member may be constituted by the guide wheel. In this case, the one-way clutch can be operated without using a component separate from a component constituting the planetary gearbox.

Further, the one-way clutch may be interposed between the guide wheel and a stationary member. In this case, the rotor of the rotor directly connected to the input shaft by the engagement of the centrifugal clutch. The low-speed rotation of the rotating shaft is permitted by sliding of a one-way clutch compactly interposed between the guide wheel and the stationary member.

[0021]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the drawings showing the embodiments. First Embodiment FIG. 1 is a first embodiment of an automotive hydraulic pump according to the present invention.
2 is a sectional view of a centrifugal clutch part of the first embodiment, and FIG. 3 is a side view of the centrifugal clutch part of the first embodiment.

The pump body 1 of the automotive hydraulic pump
Is a cam ring having an uneven thickness annular shape with a short cylindrical rotor 10 having a plurality of vanes 10a capable of moving back and forth in the radial direction.
A known vane pump which rotates inside the vane 11 and pressurizes and sends oil received between the vanes 10a, and pumps the rotor 10 and the cam ring 11 together with a pressure plate 12 which seals one side of the cam ring 11. Housing H
The pump housing H1 and the other side of the cam ring 11 are sealed by an end plate 13.

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 having one end supported by the end plate 13. As a shaft, the cam ring 11 is rotatable in the inner cavity of the cam ring 11 held between the pressure plate 12 and the end plate 13. Due to this rotation, the plurality of vanes 10a held by the rotor 10 are pushed forward and backward by pressing their respective tips against the inner peripheral surface of the cam ring 11, and are arranged side by side on the fitting periphery of the rotor 10 and the cam ring 11. The hydraulic oil in the plurality of pump chambers is sealed and rotated between the adjacent vanes 10a.

Each of the pump chambers has an end plate 13
And a suction pipe 15 attached to the peripheral surface of the pump housing H1 through a suction oil passage 14 formed in the pump housing H1. Also, each of the pump chambers
The pressure chamber 12 is connected to a pressure chamber 16 formed on the rear side of the pressure plate 12 through another through-hole penetrating the corresponding position of the pressure plate 12, and the pressure chamber 16 is formed in the pump housing H1. It communicates with a discharge pipe (not shown) through the valve chamber 17 that is provided.

In the pump body 1 configured as described above, the suction pipe 15 is connected to an oil tank containing hydraulic oil, and the discharge pipe is connected to a hydraulic actuation device such as a power steering device or an automatic transmission. The rotor 10 is rotated by the transmission from the rotor shaft 2 and used. At this time, the rotor
Each of the pump chambers lined up outside of 10 has the suction pipe 15
And the working oil is sucked through the suction oil passage 14, and as described above,
The pressure is increased while being sealed and rotated between the adjacent vanes 10a, discharged to the discharge pipe through the pressure chamber 16 and the valve chamber 17, and supplied to the hydraulic operating device.

A known flow control valve (not shown) is disposed inside the valve chamber 17, and the excess pressure oil introduced from the pressure chamber 16 into the valve chamber 17 The flow is divided by the operation of the valve and returned to the suction oil passage 14 located near the valve chamber 17.

The other end of the rotor shaft 2, which is the rotation shaft of the rotor 10, passes through the pressure plate 12 and the shaft center of the pump housing H1 that supports the rear surface of the pressure plate 12, and is fitted to the same outside of the pump housing H1. A suitable length is projected into a cylindrical transmission housing H2. An input shaft 3 is rotatably supported coaxially with the rotor shaft 2 inside the transmission housing H2. One end of the input shaft 3 is protruded by an appropriate length to the outside of the other side of the transmission housing H2, and this protruding end is not shown via a V-belt wound around a V-pulley 30 externally fitted and fixed thereto. It is linked to the output end of the engine.

The outer periphery of the middle part of the rotor shaft 2 protruding from the pump housing H1 into the transmission housing H2 is inserted into a cylindrical member of a planet carrier described later, and is supported coaxially with the input shaft 3. Around the input shaft 3, the speed increasing means 4a and the centrifugal clutch 5a
And a one-way clutch 6a.

The speed increasing means 4a in FIG. 1 is configured as a planetary gear speed increaser having a sun gear 40, a ring gear 41 and a planet gear 42. Note that the speed increasing means 4a may be a planetary roller speed increasing device including rollers corresponding to the respective gears.
Further, although other types of gearboxes can be used as the gearbox 4a, the planetary gear gearbox, the planetary roller gearbox, etc. It is desirable to use a planetary gearbox.

A sun gear (sun wheel) 40 constituting the speed increasing means 4a is a small-diameter external gear having a predetermined number of teeth on the outer peripheral surface, and is spline-fitted to the other end of the rotor shaft 2. The sun gear 40 may be integral with the rotor shaft 2.

The ring gear (guide wheel, rotating member) 41 constituting the speed increasing means 4a is a large-diameter annular internal gear having a predetermined number of teeth on its inner peripheral surface. The one-way clutch to correspond to the long direction
The planetary gear 42 is held inside the transmission housing H2 as a stationary member via 6a, and guides the revolution of the planetary gear 42 supported on the input shaft 3 via the planetary carrier 43.

Further, a planetary gear (planetary wheel) 42 constituting the speed increasing means 4a is attached to the end of the input shaft 3 which abuts on the rotor shaft 2 via a planetary carrier 43 so as to be able to rotate and revolve.

The planet carrier 43 comprises a disc member 43a connected to the other end of the input shaft 3 by a press-fitting means or the like, and a plurality of connecting shaft portions 43b protruding from one surface of the disc member 43a. And a cylindrical member 43c coupled to the disk member 43a via a sliding member 43d. The cylindrical member 43c is rotatably fitted to the outer periphery of the middle part of the rotor shaft 2 via a slide bearing 43d.
A flange 43e is formed at one end of the cylindrical member 43c so as to face one surface of the disk member 43a, and a screw 44 is inserted into a hole formed in the flange 43e and the connecting shaft 43b. The disk member 43a and the cylindrical member 43c are connected.

The planetary gear 42 is an external gear having a predetermined number of teeth on its outer peripheral surface.
The shaft 41 and the shaft member 41 are aligned with each other in the axial direction, and are freely rotatably supported by a support shaft 45 provided between the disk member 43a and the flange 43e.

Although only one planetary gear 42 is shown in FIG. 1, a plurality of (generally three or four) planetary gears 42, 42 are provided around the planetary carrier 43. Are equidistantly supported, and are meshed with the inner sun gear 40 and the outer ring gear 41 at respective circumferential positions.

The one-way clutch 6a interposed between the ring gear 41, which is a rotating member (guide wheel), and the inside of the transmission housing H2 includes a fixed wheel 61 fitted and fixed inside the transmission housing H2. A plurality of engaging members 62 arranged in the circumferential direction inside the fixed ring 61 and capable of operating to the locked position / unlocked position, and a holding member 63 holding the engaging members 62 and having a fitting hole. The engaging element 62 is moved to the lock position by the counter-rotating torque (in the direction of arrow Y in FIG. 5) applied to the ring gear 41 via the rotor shaft 2, the sun gear 40 and the planetary gear 42, and the rotation of the ring gear 41 is stopped. ing. Therefore, the ring gear is connected via the planet carrier 43 and the planet gear 42.
The ring gear 41 does not rotate when the rotational torque applied to the 41 (in the direction of the arrow X in FIG. 5) is equal to or less than the anti-rotation torque (reverse rotation torque> rotation torque). Further, when the input shaft 3 and the rotor shaft 2 are directly connected by the engagement of the centrifugal clutch 5a, and the rotational torque applied to the ring gear 41 via the planetary carrier 43 and the planetary gear 42 exceeds the anti-rotational torque (reverse rotation) (Rotation torque <rotation torque), the engaging element 62 moves to the unlocked position, and the ring gear 41 moves to the planet gear 42 and the planet carrier 43.
It rotates together with it to cut off the transmission with increased speed.

A centrifugal clutch 5a having a cam ring 55, a clutch shoe 51, and a clutch drum 52 is provided side by side on one side of the speed increasing means 4a (the side on which the pump body 1 is mounted) constructed as described above. The cam ring 55 is externally fitted and fixed to the cylindrical member 43c of the planet carrier 43,
The cam ring 55 has two substantially circular support plates 56, 56 at both ends thereof.

The clutch shoe 51 is formed in a substantially arc shape, and the cam ring 55 having a cam 55a on the outer peripheral surface.
Are supported via a support shaft 57 so as to be able to swing in the radial direction. Such a clutch shoe
A plurality of 51s are arranged in the circumferential direction of the cam ring 55, and the swing of each clutch shoe 51 is suppressed by a spring 58 interposed between the clutch shoe 51 and the support shaft 57. Also cam ring
A rolling element 59 that engages with the cam 55a of the cam ring 55 when the clutch shoe 51 is pressed against the clutch drum 52 is interposed between the outer peripheral surface of 55 and the clutch shoe 51. Further, a friction plate 54 having a large friction coefficient is attached to the outer surface of the circular arc of each clutch shoe 51.

Further, as shown in FIG. 1, the clutch drum 52 has a short-diameter, large-diameter drum shape obtained by bending the outer peripheral portion of a thin-walled disk having a fitting cylindrical portion 52a at the center portion at a substantially right angle. Positioned so as to surround the outside of the clutch shoe 51 by the cylindrical portion 52b, the fitting cylindrical portion 52a is
, And is adapted to rotate integrally with the rotor shaft 2.

FIGS. 4 and 5 are explanatory diagrams of the operation of the automotive hydraulic pump according to the present invention including the speed increasing means 4a, the centrifugal clutch 5a and the one-way clutch 6a configured as described above. Shows a state in which the input shaft 3 is rotating at a low speed due to transmission from the engine via the V pulley 30.

At this time, the speed increasing means together with the input shaft 3
The planet carrier 43 of FIG. 4a rotates (revolves) in the clockwise direction (the direction of arrow X) in FIG. 5, and the plurality of planet gears 42, 42 supported by the planet carrier 43 are connected to the sun gear 40 and the ring gear 41. While maintaining the meshing, it rotates (self-rotates) around each other support shaft 45 in the counterclockwise direction (arrow Y direction) in FIG. Also, since a load necessary for rotating the rotor 10 is applied to the planet gears 42 via the rotor shaft 2 and the sun gear 40, when the planet gears 42 rotate in the arrow Y direction, An anti-rotation torque in the direction of arrow Y is applied to the ring gear 41, and the anti-rotation torque causes the engaging element 62 of the one-way clutch 6a to move to the lock side, so that the ring gear 41 is restrained from rotating. Here, the planetary gears 42, 42
The rotational force of the inner sun gear 40 is applied by the rotation of..., And the sun gear 40 includes the ring gear 41 and the planetary gears 42, 42,.
The rotation speed is increased according to the gear ratio. Due to such rotation of the sun gear 40, the rotor shaft 2 rotates at a high speed together with the sun gear 40 at a speed sufficiently higher than that of the input shaft 3.

At this time, the clutch shoe 51 of the centrifugal clutch 5a rotates together with the input shaft 3, and a centrifugal force accompanying the rotation of the input shaft 3 acts on the clutch shoe 51. This centrifugal force is small. The clutch shoe 51 is pulled inward by the spring force of the spring 58, is separated from the clutch drum 52 that rotates integrally with the rotor shaft 2, and the rotation is not transmitted through the centrifugal clutch 5a.

FIG. 4B shows a V pulley from the engine.
The state where the input shaft 3 is rotating at a high speed by the transmission via 30 is shown.

At this time, the clutch shoe 51 of the centrifugal clutch 5a which rotates together with the input shaft 3 via the planet carrier 43.
A large centrifugal force acts on the clutch shoe 51, and the clutch shoe 51 pivots outward in the radial direction against the spring force of the spring 58 and presses against the inner peripheral surface of the clutch drum 52 surrounding the outside. Can be With this pressing, the clutch shoe 51
The clutch drum 52 is engaged with the clutch drum 51 via the friction plate 54 having a high coefficient of friction applied to the outer surface of the circular arc of the clutch shoe 51 so that the clutch drum 52 is integrally rotated. The rotated rotor shaft 2 rotates at a low speed at the same speed as the input shaft 3 that rotates integrally with the clutch shoe 51 via the planet carrier 43.

At this time, the planetary gears 42, 42 are engaged with the sun gear 40 and the ring gear 41, but the rotation of the input shaft 3 is directly transmitted to the rotor shaft 2 via the planetary carrier 43 and the centrifugal clutch 5a. As a result, the rotational torque applied to the ring gear 41 via the planet carrier 43 and the planet gears 42 exceeds the anti-rotation torque, and the rotational torque causes the engaging element 62 of the one-way clutch 6a to move to the unlock position. , The ring gear 41 rotates together with the planetary gears 42 and the planetary carrier 43, and the planetary gears 42, 42,.
Transmission at speed increase to 40 is cut off.

As described above, in the automotive hydraulic pump according to the present invention, the transmission from the input shaft 3 to the rotor shaft 2 is performed between the two via the speed increasing means 4a and the centrifugal clutch 5a configured as described above. When the input shaft 3 is rotating at a low speed, the rotor shaft 2 is driven to rotate at a speed sufficiently higher than the input shaft 3 by the operation of the speed increasing means 4a, and is connected to the discharge side of the pump body 1. A desired operating oil pressure can be supplied to the operated hydraulic operating device.

On the other hand, the rotor shaft 2 during the high-speed rotation of the input shaft 3 is directly connected to the input shaft 3 by the engagement of the centrifugal clutch 5a, and the transmission at the increased speed by the speed increasing means 4a is transmitted to the one-way clutch. The drive is interrupted by 6a and driven at the same speed as the input shaft 3, so that the power loss of the engine for this drive can be reduced as much as possible.

FIG. 6 is a diagram showing the discharge flow rate characteristics of the pump body 1. In the automotive hydraulic pump according to the present invention in which the transmission is performed as described above, in the region where the rotational speed of the input shaft 3 is low as shown on the horizontal axis in FIG. It rotates at a high speed and shows a characteristic that the discharge flow rate sharply increases. On the other hand, after the rotation speed of the input shaft 3 increases and the centrifugal clutch 5a is engaged, the rotation speed of the rotor shaft 2 decreases due to the direct connection with the input shaft 3, so that the discharge flow rate decreases.

The rotation speed of the rotor shaft 2 after the centrifugal clutch 5a is engaged increases as the rotation speed of the input shaft 3 increases. As a result, the actual discharge flow rate of the pump body 1 is indicated by a broken line in FIG. The gradual increase is returned to the suction oil passage 14 by the operation of the flow control valve disposed in the valve chamber 17, and the discharge flow rate in the high-speed rotation region is constant as shown in FIG. Will be kept.

Second Embodiment FIG. 7 is a second embodiment of the automotive hydraulic pump according to the present invention.
FIG. The vehicle hydraulic pump according to the second embodiment includes a clutch shoe 51 of the centrifugal clutch 5a provided on the planetary carrier 43, and a clutch shoe 51 provided on the rotor shaft 2 instead of the clutch drum 52 provided on the rotor shaft 2. 52 is provided in the planet carrier 43.

In the second embodiment, the cam ring 55
Are fitted and fixed in the middle of the rotor shaft 2, and the clutch shoe 51 supported by the cam ring 55 is attached to the rotor shaft 2.
It is made to rotate integrally with.

The clutch drum 52 is connected to a disc-shaped planetary carrier 43 integrally formed at the other end of the input shaft 3 by a plurality of connecting shaft portions 43b and the male screw 44.
The input shaft 3 rotates integrally with the input shaft 3 via the planet carrier 43. The other end of the rotor shaft 2 is supported via a bearing in a support hole 3a formed in the other end of the input shaft 3.

In the second embodiment, the planet carrier 43 and the clutch drum 52 rotate together with the input shaft 3,
Further, the rotation of the input shaft 3 causes the planet carrier 43, the planet gears 42,
Are transmitted to the rotor shaft 2 via the sun gear 40 and the sun shaft 40, and the rotor shaft 2 rotates together with the sun gear 40 at a speed sufficiently higher than that of the input shaft 3.

At this time, the clutch shoe 51 of the centrifugal clutch 5a rotates together with the rotor shaft 2, and a centrifugal force associated with the rotation of the rotor shaft 2 acts on the clutch shoe 51. The clutch shoe 51 is pulled inward by the spring force of the spring 58, is separated from the clutch drum 52 that rotates integrally with the input shaft 3, and the rotation is not transmitted through the centrifugal clutch 5a. When the rotation torque applied to the ring gear 41 is equal to or less than the anti-rotation torque, the ring gear 41 is restrained from rotating.

When the input shaft 3 rotates at a high speed, a large centrifugal force acts on the clutch shoe 51 of the centrifugal clutch 5a which rotates together with the rotor shaft 2, and the clutch shoe 51 moves on the inner circumference of the clutch drum 52. Pressed against the surface. By this pressing, the clutch shoe 51 and the clutch drum 52 are engaged via the friction plate 54 and rotate integrally with each other, and the rotor shaft 2 provided with the clutch shoe 51 is Clutch drum 52
It rotates at a low speed at the same speed as the input shaft 3 that rotates integrally with the input shaft 3.

At this time, the rotation of the input shaft 3 is directly transmitted to the rotor shaft 2 via the planet carrier 43 and the centrifugal clutch 5a, so that the rotational torque applied to the ring gear 41 via the planet carrier 43 and the planet gears 42. However, the torque exceeds the anti-rotation torque, and the engagement torque of the one-way clutch 6a moves to the unlock position by the rotation torque,
The ring gear 41 rotates together with the planetary gears 42 and the planetary carrier 43, and transmission from the planetary gears 42, 42,.

Since other structures and operations are the same as those of the first embodiment, the same parts are denoted by the same reference numerals.
The detailed description and the function and effect will be omitted.

In the above-described embodiment, when the input shaft 3 and the rotor shaft 2 are directly connected by the engagement of the centrifugal clutch 5a, the transmission by the speed increasing means 4a is transmitted to the one-way clutch.
6a, the rotation of the ring gear 41, which is a rotating member, is stopped when the reverse rotation torque> rotation torque is satisfied instead of the one-way clutch 6a, and the reverse rotation torque <rotation torque is satisfied. When the ring gear 41
May be used, and the configuration of the clutch is not particularly limited.

Third Embodiment FIG. 8 shows a third embodiment of the automotive hydraulic pump according to the present invention.
FIG. The vehicle hydraulic pump according to the third embodiment is different from the sun gear 40 of the speed increasing means 4 in that the one-way clutch 6a is interposed between the ring gear 41 of the speed increasing means 4a and the transmission housing H2 as a stationary member. A one-way clutch 6 is interposed between the rotor shaft 2.

In the third embodiment, around the rotor shaft 2 and the input shaft 3, a speed increasing means 4, a centrifugal clutch 5, and a one-way clutch 6, which are features of the present invention, are provided.

The sun gear 40 constituting the speed increasing means 4 is a small-diameter external gear having a predetermined number of teeth on the outer peripheral surface. The sun gear 40 is externally fitted on the outer periphery of the middle part of the rotor shaft 2 via the one-way clutch 6. Have been. The one-way clutch 6 is a known mechanical element having a plurality of engaging members arranged in a circumferential direction, and the rotor shaft 2 and the sun gear 40 are engaged via the engaging members only during transmission from the latter to the former. It is made to rotate together when combined.

The ring gear 41 constituting the speed increasing means 4
Is a large-diameter annular internal gear having a predetermined number of teeth on its inner peripheral surface, which is fitted and fixed inside the transmission housing H2 so as to correspond to the mounting position of the sun gear 40 in the axial direction. I have.

The planetary gear 42 constituting the speed increasing means 4 is
The input shaft 3 is mounted via a planet carrier 43 in the vicinity of the end where the input shaft 3 abuts on the rotor shaft 2. The planet carrier 43,
The input shaft 3 is spline-coupled to the corresponding position of the input shaft 3.
This is a disk-shaped member that rotates integrally with the member. The planetary gear 42
Is an external gear having a predetermined number of teeth on the outer peripheral surface thereof. The support gear is arranged on a predetermined circumference of one surface of the planetary carrier 43 so as to be aligned with the sun gear 40 and the ring gear 41 in the axial direction. It is freely rotatably supported on a shaft.

Although only one planetary gear 42 is shown in FIG. 8, a plurality (generally three or four) of planetary gears 42, 42 are provided around the planetary carrier 43. Are equidistantly supported, and are meshed with the inner sun gear 40 and the outer ring gear 41 at respective circumferential positions.

On one side of the speed increasing means 4 (the side on which the pump body 1 is mounted) constructed as described above, a centrifugal clutch 5 having a rotary plate 50, a clutch shoe 51 and a clutch drum 52 is provided.
Are juxtaposed. The rotating plate 50 is a member having a hollow disk shape, and is provided on one surface of the planet carrier 43 of the speed increasing means 4.
A plurality of connecting pins 50a, 50a... (Only one is shown) which are driven out of the supporting positions of the planetary gears 42, 42... (Only one is shown) so as to rotate integrally with the input shaft 3 together with the planetary carrier 43. There is something.

The rotation of the clutch shoe 51 is restricted by the guide pins 50b provided on the other surface (the surface on the pump body 1 side) of the rotary plate 50 as described above, and the clutch shoe 51 is movable radially outward. It is supported by. A plurality of such clutch shoes 51 are arranged in the circumferential direction of the rotating plate 50.These clutch shoes 51 are radially inwardly directed by ring springs 53 inserted and held in annular grooves provided on the respective side surfaces. It is energized all at once. Further, a friction plate 54 having a large friction coefficient is attached to the outer peripheral surface of each clutch shoe 51.

Further, as shown in FIG. 8, the clutch drum 52 has a short-diameter, large-diameter drum shape obtained by bending the outer peripheral portion of a thin-walled disk at a substantially right angle.
The rotor shaft 2 is positioned so as to surround the outside of the transmission shaft 51 and is spline-coupled to an intermediate portion of the rotor shaft 2 projecting into the transmission housing H2 so as to rotate integrally with the rotor shaft 2.

FIG. 9 is an operation explanatory diagram of the third embodiment of the automotive hydraulic pump according to the present invention including the speed increasing means 4, the centrifugal clutch 5, and the one-way clutch 6 configured as described above. (A) shows a V pulley 30 from the engine.
Shows a state in which the input shaft 3 is rotating at a low speed due to the transmission via.

At this time, together with the input shaft 3, the speed increasing means 4
Of the planet carrier 43 rotates (revolves), and the planet carrier 43
Are supported by the sun gears.
It rotates (self-rotates) around each other support shaft while maintaining engagement with the ring gear 41 and the ring gear 41. Here, since the outer ring gear 41 is restricted so as not to rotate, the planetary gears 42, 42
The rotational force of the inner sun gear 40 is applied by the rotation of..., And the sun gear 40 includes the ring gear 41 and the planetary gears 42, 42,.
The rotation speed is increased according to the gear ratio. By the rotation of the sun gear 40, the one-way clutch 6 interposed in the fitting portion with the rotor shaft 2 is engaged, and the rotor shaft 2 and the sun gear 40 are sufficiently larger than the input shaft 3 together. It rotates at a high speed.

At this time, the clutch shoe 51 of the centrifugal clutch 5 rotates together with the input shaft 3, and a centrifugal force accompanying the rotation of the input shaft 3 acts on the clutch shoe 51.
This centrifugal force is small, and the clutch shoe 51 is pulled inward by the spring force of a ring spring 53 shown as a spring body in FIG.
And the rotation is not transmitted through the centrifugal clutch 5.

FIG. 9B shows a V pulley from the engine.
The state where the input shaft 3 is rotating at a high speed by the transmission via 30 is shown.

At this time, a large centrifugal force acts on the clutch shoe 51 of the centrifugal clutch 5 that rotates together with the input shaft 3, and the clutch shoe 51 resists the spring force of the ring spring 53 and the guide pin 50 b. The clutch drum which moves radially outward under the guidance of
It is pressed against the inner peripheral surface of 52. By this pressing, the clutch shoe 51 and the clutch drum 52 are engaged with each other via the friction plate 54 having a high coefficient of friction applied to the outer periphery of the former, so that the clutch shoe 51 and the clutch drum 52 rotate integrally with each other.
The rotor shaft 2 with the fitted 52 rotates at a low speed at the same speed as the input shaft 3 that rotates integrally with the clutch shoe 51.

At this time, in the speed increasing means 4, the revolution of the planet carrier 43 that rotates integrally with the input shaft 3,
Planetary gears 42, 42 between the sun gear 40 and the ring gear 41 ...
Speed is transmitted to the sun gear 40 through the rotation of the
The sun gear 40 rotates at a high speed, but the rotation is not transmitted to the rotor shaft 2 due to the slip of the one-way clutch 6 interposed between the sun gear 40 and the sun gear 40.
Due to the engagement of the centrifugal clutch 5, the rotor idles on the circumference of the rotor shaft 2 which rotates at a low speed.

As described above, in the automotive hydraulic pump according to the third embodiment, the transmission from the input shaft 3 to the rotor shaft 2 is transmitted between the speed increasing means 4, the centrifugal clutch 5 and the one The operation of the speed increasing means 4 causes the rotation of the rotor shaft 2 at a speed sufficiently higher than that of the input shaft 3, whereby the rotation of the rotor shaft 2 is performed via the directional clutch 6. A desired operating oil pressure can be supplied to a hydraulic operating device connected to the discharge side of the main body 1.

On the other hand, the rotor shaft 2 during the high-speed rotation of the input shaft 3 is directly connected to the input shaft 3 by engagement of the centrifugal clutch 5, bypassing the speed increasing means 4, and has the same speed as the input shaft 3. The power loss of the engine for this drive can be reduced as much as possible.

Since other structures and operations are the same as those of the first embodiment, the same parts are denoted by the same reference numerals.
The detailed description and the function and effect will be omitted.

In the above embodiment, the case where the pump main body 1 is provided as a vane pump has been described, but it goes without saying that the pump main body 1 may be another type of pump such as a gear pump.

[0078]

As described in detail above, according to the first, third and fourth aspects of the present invention, the switching of the rotational speed in accordance with the level of the engine speed can be reliably realized with a simple configuration. Can be.

According to the second and fifth aspects of the present invention, the transmission system including the centrifugal clutch can be compactly arranged around the input shaft and the rotary shaft, and the size required for mounting the vehicle can be reduced. The present invention has excellent effects, for example, it can meet the requirements of the above.

[Brief description of the drawings]

FIG. 1 is a side sectional view of Embodiment 1 of a vehicle hydraulic pump according to the present invention.

FIG. 2 is a sectional view of a centrifugal clutch part of the first embodiment of the automotive hydraulic pump according to the present invention.

FIG. 3 is a side view of a centrifugal clutch part of the automotive hydraulic pump according to the first embodiment of the present invention.

FIG. 4 is an operation explanatory view of Embodiment 1 of the automotive hydraulic pump according to the present invention.

FIG. 5 is an operation explanatory diagram of Embodiment 1 of the automotive hydraulic pump according to the present invention.

FIG. 6 is a view showing a discharge flow rate characteristic of a pump body.

FIG. 7 is a side sectional view of Embodiment 2 of the automotive hydraulic pump according to the present invention.

FIG. 8 is a side sectional view of a third embodiment of the automotive hydraulic pump according to the present invention.

FIG. 9 is an operation explanatory view of Embodiment 3 of the automotive hydraulic pump according to the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Pump main body (automobile hydraulic pump) 2 Rotor shaft (rotating shaft) 3 Input shaft 4, 4a Speed increasing means (planet gearbox) 5, 5a Centrifugal clutch 6, 6a One-way clutch (clutch) 10 Rotor 40 Sun gear ( Sun wheel) 41 Ring gear (guide wheel, rotating member) 42 Planetary gear (planetary wheel) 43, 43a Planet carrier 51 Clutch shoe 52 Clutch drum H2 Transmission housing (stationary member)

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor 3-5-8 Minamisenba, Chuo-ku, Osaka-shi, Osaka Prefecture F-term in Koyo Seiko Co., Ltd. 3D033 EB02 3J027 FA19 FB40 GA01 GB03 GC13 GC22 GD04 GD07 GD08 3J068 AA01 AA05 BA14 CA02 CB03 GA19

Claims (5)

[Claims] 1. An automotive hydraulic pump, comprising: an input shaft; and a rotor that rotates by transmission from the input shaft, wherein the rotation of the rotor generates hydraulic pressure supplied to a hydraulic operating device mounted on the vehicle. A speed increasing means disposed between the rotation shaft of the rotor and the input shaft for speeding up the rotation of the input shaft and transmitting the rotation to the rotation shaft; A centrifugal clutch that directly connects the input shaft and the rotary shaft, and operates to cut off transmission by the speed increasing means when the input shaft and the rotary shaft are directly connected by engagement of the centrifugal clutch. An automotive hydraulic pump comprising a clutch. 2. The hydraulic pump according to claim 1, wherein the clutch is interposed between the speed increasing means and a stationary member provided near the speed increasing means. 3. The speed increasing means applies a reverse rotation torque when the rotation of the input shaft is increased and transmitted to the rotation shaft, and when the input shaft and the rotation shaft are directly connected, the reverse rotation torque is reduced. Has a rotating member to which a large rotating torque is applied, the clutch stops the rotation of the rotating member when the reverse rotating torque is larger than the rotating torque, and stops the rotation of the rotating member when the reverse rotating torque is smaller than the rotating torque. 3. The hydraulic pump according to claim 1, wherein the hydraulic pump is a one-way clutch. 4. An automotive hydraulic pump, comprising: an input shaft; and a rotor that rotates by transmission from the input shaft, wherein the rotation of the rotor generates hydraulic pressure supplied to a hydraulic operating device mounted on the vehicle. A speed increasing means disposed between the rotating shaft of the rotor and the input shaft to increase the speed of rotation of the input shaft and to transmit the rotation to the rotating shaft; A centrifugal clutch engaged by the action of centrifugal force accompanying rotation and directly connecting the input shaft and the rotary shaft; and a centrifugal clutch interposed between the input shaft or the rotary shaft and the speed increasing means. A hydraulic pump for an automobile, comprising: a one-way clutch that operates in response to a decrease in the speed of the rotating shaft due to engagement and that interrupts transmission between the input shaft or the rotating shaft and the speed increasing means. . 5. A speed increasing means comprising: a sun wheel rotating integrally with the rotating shaft; a planet wheel supported on the input shaft via a planet carrier and revolving by engaging with the sun wheel; The automotive hydraulic pump according to any one of claims 1, 2, and 4, comprising a planetary gearbox having guide wheels for guiding the revolution of the vehicle.