JP3775912B2 - Hydraulic pump for automobile - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a hydraulic pump for an automobile driven by an engine so as to generate a supply hydraulic pressure to a hydraulic actuator mounted on the automobile.
[0002]
[Prior art]
2. Description of the Related Art Recent automobiles are equipped with various devices that operate 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 automobile hydraulic pumps use part of the power generated by the on-board engine, and are driven by belt transmission via a power take-off pulley provided at the end of the crankshaft of the engine, for example. However, with such a simple transmission configuration, there is a disadvantage that the power loss for driving the hydraulic pump is large and the fuel consumption is reduced when the engine is running at a high speed. When the specification of the hydraulic pump is determined so as to reduce the pressure, there is a problem that when the engine runs at a low speed or when the engine speed is low or the vehicle stops, the capacity of the hydraulic pump becomes insufficient and sufficient hydraulic pressure cannot be obtained.
[0004]
As described above, in an automobile hydraulic pump that is used to generate hydraulic pressure supplied to a hydraulic actuator mounted on an automobile, inadvertent power loss of an engine serving as a driving source is ensured while ensuring sufficient hydraulic pressure when necessary. In order to meet this requirement, the following two configurations have been disclosed.
[0005]
In the first configuration, for example, in a hydraulic power steering device that assists the force required for steering by hydraulic pressure, it is necessary to supply hydraulic pressure only at the time of steering. However, as disclosed in Japanese Patent Application Laid-Open No. 57-15064 and the like for a power steering device, a hydraulic pump for supplying the operating hydraulic pressure is not required. A clutch is interposed in the middle of the transmission system to one hydraulic pump, and the clutch is engaged and controlled according to the detection result of the running state such as the rotational speed of the engine and the steering state. One, two hydraulic pumps are driven only when necessary.
[0006]
In this configuration, one hydraulic pump is always driven in order to prevent the hydraulic oil from becoming highly viscous when the outside air temperature is low by constantly generating a flow of hydraulic oil. By making the hydraulic pump that is always driven small in capacity, it is possible to reduce power loss as much as possible.
[0007]
In the second configuration, a ring cone type continuously variable transmission is arranged between an input shaft linked to an engine and a rotor shaft of a hydraulic pump, as disclosed in JP-A-7-133854 and the like. The speed change 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, and this rotation is performed when the engine is rotating at low speed. Is transmitted to the hydraulic pump as it is, and at the time of high-speed rotation of the engine, it is transmitted to the hydraulic pump after a predetermined deceleration, thereby simultaneously reducing power loss during high-speed driving and eliminating hydraulic oil shortage during low-speed driving. It is what I did.
[0008]
As the continuously variable transmission disposed between the input shaft and the rotor shaft, other types of continuously variable transmissions such as a variable pitch pulley type can be used instead of the ring cone type continuously variable transmission described above. In addition, the change of the transmission gear ratio can be realized by using an appropriate actuator that operates according to the detection result of the running state of the automobile such as the rotational speed of the engine, the state of steering, and the like. Has also been proposed.
[0009]
[Problems to be solved by the invention]
However, in the first configuration, two hydraulic pumps, a transmission system between these and the engine, and a clutch interposed in one transmission system are required, and further, a sensor for detecting a running state, A control device for engaging and disengaging the clutch based on the detection result of the sensor is required, which complicates the overall configuration and may cause malfunction due to the influence of external noise.
[0010]
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 by the action of centrifugal force, there is no possibility of malfunction due to the influence of external noise. However, there is a problem that it is difficult to reduce the size of the continuously variable transmission including the transmission means, and instead of the ring cone type continuously variable transmission, other types of continuously variable transmissions are required in order to reduce the size. Is used, a great amount of force is required to change the gear ratio, and there is a problem that it is difficult to realize a mechanical transmission means by the action of centrifugal force.
[0011]
In addition, in this configuration, only the gear ratio is changed according to 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 loss in a rough running state.
[0012]
As described above, this problem can be solved by using an appropriate actuator that operates in accordance with the detection result of the running state of the automobile for realizing the shift, and the shift using this type of actuator is other than the ring cone type. However, in this case, as in the first configuration, the sensor for detecting the running state, and the actuator based on the detection result of the sensor can be realized. A control device for control is required, resulting in a complicated overall configuration and a possibility of malfunction due to the influence of external noise.
[0013]
The present invention has been made in view of such circumstances, and a sensor for detecting a running state, a shift according to the operating state of the hydraulic actuator, and a shift according to the rotational speed of the engine serving as a drive source, and the sensor Control means according to the detection result is not required, it can be realized by mechanical means together, ensuring sufficient supply oil pressure only when necessary, and ineffective power loss of the engine as the drive source is possible An object of the present invention is to provide a hydraulic pump for an automobile that can be alleviated.
[0014]
[Means for Solving the Problems]
  An automotive hydraulic pump according to the present invention includes a rotor that rotates by transmission from an input shaft that is linked to an output end of an engine, and generates hydraulic pressure supplied to a hydraulic actuator mounted on the automobile. In the above, it is arranged between the input shaft and the rotor, and the gear ratio between them is set.A constant speed position where the rotation of the input shaft is transmitted to the rotor at a constant speed and a deceleration position where the rotation of the input shaft is transmitted to the rotor at a reduced speed.Shifting means for switching;Ascending according to the operation of the hydraulic actuatorDue to the action of the supply hydraulic pressure, the transmission meansTo the constant velocity positionAnd a hydraulic clutch for performing a switching operation.
[0015]
  In the present invention, it is utilized that the hydraulic pressure generated by the hydraulic pump for an automobile changes according to the operating state of the hydraulic actuator that is the supply destination, and rises during operation and decreases during non-operation. During the operation of the hydraulic actuator that requires hydraulic supply, the hydraulic clutch operates by the action of the supply hydraulic pressure that rises along with this, and the transmission means arranged between the input shaft from the engine and the rotating shaft of the rotorAt constant speedThe rotation speed of the rotorHigh speed equal to the input shaftEnsure sufficient supply hydraulic pressure. In addition, during the non-operation of the hydraulic actuator that does not require hydraulic supply, the supply hydraulic pressure that decreases with this operation is affected.BeforeThe speed change meansDeceleration positionThe rotation speed of the rotorThan the rotation speed of the input shaftThis reduces the power loss of the engine that is the driving source.
[0016]
  Further, it moves by the action of centrifugal force accompanying the rotation of the input shaft, releases the working pressure to the hydraulic clutch,Constant speed positionA centrifugal spool for prohibiting the switching operation is provided.
[0017]
  In this invention, when the rotation of the input shaft linked to the output end of the engine becomes excessive, the centrifugal spool moves due to the centrifugal force caused by the rotation, and the transmission meansConstant speed positionThe switching operation is prohibited, preventing an excessive increase in the rotational speed of the rotor and reducing the power loss of the engine serving as the drive source. At this time, the rotational speed of the input shaft is transmitted to the rotor after being decelerated by the speed change means. However, since the rotational speed of the input shaft itself is high, the rotational speed of the rotor is kept high to some extent, Supply hydraulic pressure is sufficiently secured.
[0018]
The working pressure release oil passage includes a variable throttle that changes a throttle area by a control edge formed in a part of the centrifugal spool, and a fixed throttle that adds a predetermined throttle resistance to the pressure oil that has passed through the variable throttle. It is characterized by providing.
[0019]
In this invention, when the centrifugal spool moves in accordance with the increase in the rotational speed of the input shaft, the working pressure to the hydraulic clutch passes through the variable throttle that changes the throttle area by the control edge formed on the centrifugal spool, It is released through the fixed throttle. As a result, the steep change in the working pressure is alleviated and the switching operation of the hydraulic clutch is not performed rapidly, discontinuity of the pressure characteristic on the discharge side of the hydraulic pump is eliminated, and a smooth pressure characteristic is obtained. This change mode can be easily adjusted by additional processing of the control edge and the fixed restrictor, and a desired pressure characteristic can be obtained.
[0020]
Further, the speed change means is arranged coaxially between the planetary body held by a carriage that rotates integrally with the rotation shaft of the rotor, and between the rotation shaft and the input shaft, and is arranged inside each planetary body. And a one-way clutch interposed between the solar disk and the input shaft, and allowing the sun disk to rotate in advance, wherein the hydraulic clutch is integrated with the carriage. A rotating clutch plate, and a piston that is constrained to rotate by the input shaft, moves in the axial length direction by the action of the supply hydraulic pressure, and is pressed against the clutch plate.
[0021]
In this invention, the speed change means between the input shaft and the rotor is provided with the planetary body and the solar disk, and normally, the rotation of the input shaft is performed via the solar disk, the planetary body and these carriages. As a planetary roller transmission or planetary gear transmission that decelerates and transmits the rotation to the rotating shaft of the rotor, a compact configuration is formed between the input shaft and the rotor. The switching of the speed change means to the high speed side includes a clutch plate that rotates integrally with the carriage, and a piston that is constrained to rotate by the 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 constraining the rotation shaft of the rotor through a carriage that rotates integrally with the clutch plate and rotating it at a constant speed with the input shaft by the operation of a hydraulic clutch that is compactly constructed on one side of the transmission means. Note that the preceding rotation that occurs with respect to the input shaft in the solar disk that is in rolling contact with the planetary body due to the restraint of the carriage is permitted by a one-way clutch interposed between the solar disk and the input shaft.
[0022]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described in detail with reference to the drawings illustrating embodiments thereof. FIG. 1 is a longitudinal sectional view showing a first embodiment of an automotive hydraulic pump according to the present invention.
[0023]
The illustrated hydraulic pump for an automobile includes a pump main body 1 configured as a vane pump including a short cylindrical rotor 10 including a plurality of vanes that can be moved back and forth in a radial direction, and a cam ring 11 having an uneven annular shape. ing. The cam ring 11 is housed inside the pump housing 14 together with a pressure plate 12 that is coaxially positioned on one side of the cam ring 11, and between the end plate 13 and the pressure plate 12 that closes the other side of the pump housing 14. It is held and fixed.
[0024]
The rotor 10 passes through the axial center portion of the pressure plate 12 and the cam ring 11 and is splined to the middle portion of the rotor shaft 2 supported by the end plate 13. The rotor shaft 2 is used as a rotation shaft. The cam plate 11 rotates between the pressure plate 12 and the end plate 13 so as to rotate.
[0025]
Inside the cam ring 11, a plurality of recesses are provided in the circumferential direction, 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 outward in the radial direction 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. Thus, the rotation of the rotor 10 accompanying the rotation of the rotor shaft 2 is performed while maintaining the pressed state of each vane.
[0026]
Each of the pump chambers communicates with a suction pipe 15 attached to the outside of the pump housing 14 through a suction oil passage 16 formed in the peripheral wall of the pump housing 14 and the end plate 13, and the pressure plate 12 A pressure chamber 17 formed on the back side and a discharge chamber 18 drilled in the pump housing 14 are connected to a discharge pipe (not shown). This discharge pipe is a hydraulic steering destination such as a power steering device. In addition, the suction pipe 15 is connected to an oil tank that stores hydraulic oil of the hydraulic actuator.
[0027]
Thus, when the rotor 10 rotates with the rotation of the rotor shaft 2, hydraulic oil is introduced into the pump chambers arranged outside the rotor 10 through the suction pipe 15 and the suction oil passage 16. This introduced oil is sealed between the adjacent vanes, and is pressurized while being rotated together with the rotor 10, and is discharged to the discharge pipe through the pressure chamber 17 and the discharge chamber 18, and supplied to an appropriate hydraulic actuator. Is done.
[0028]
  The rotor shaft 2 which is the rotation shaft of the rotor 10 penetrates the pump housing 14 on the pressure chamber 17 side and protrudes to the outside by an appropriate length. A transmission housing 19 is coaxially assembled to the end of the pump housing 14 on the same side.RecordAn input shaft 3 is supported so as to be rotatable coaxially with the rotor shaft 2. One end of the input shaft 3 protrudes to the outside of the transmission housing 19 by an appropriate length, and is not shown through 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.
[0029]
The other end portion of the input shaft 3 extending in the transmission housing 19 is abutted against the end portion of the rotor shaft 2 protruding from the pump housing 14, and a transmission chamber 4 having a circular cross section is formed around these ends. A transmission means 5 and a hydraulic clutch 6 which are the characteristics of the present invention are formed inside the transmission chamber 4.
[0030]
  The illustrated transmission means 5 includes a planetary roller including a sun roller 50, a planetary roller 51, and a fixing ring 52.Equipped with reducering. The sun roller 50 is a disk having an appropriate thickness. The sun roller 50 is interposed between the butted ends of the rotor shaft 2 and the input shaft 3, and supports the shafts 2 and 3 protruding on both sides in the thickness direction. It is supported on the same axis as these while being held at the axial center.
[0031]
The sun roller 50 is supported on the rotor shaft 2 side by a bush fitted and fixed to the shaft center portion of the rotor shaft 2 so as to be relatively rotatable. On the other hand, a one-way clutch 20 that permits the preceding rotation of the sun roller 50 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 by the engagement of the one-way clutch 20 at the normal time when the rotation of the input shaft 3 precedes. In a state preceding the rotation, the one-way clutch 20 can be disengaged to freely rotate between the rotor shaft 2 and the input shaft 3 without being constrained by both of them. .
[0032]
The fixing ring 52 is fitted and fixed to the inside of the transmission chamber 4 at a position substantially aligned with the arrangement position of the sun roller 50 in the axial direction, and a plurality of fixing rings 52 are provided between the fixing ring 52 and the sun roller 50. Are arranged at substantially equal intervals in the circumferential direction. These planetary rollers 51, 51... Are rotatably attached to different spindles protruding from one surface of a disk-shaped carriage 53 coaxially splined to the end of the rotor shaft 2. The outer peripheral surface of 50 and the inner peripheral surface of the fixing ring 52 are brought into rolling contact with each other, and revolve around the axis of the rotor shaft 2 together with the carriage 53 while rotating around the respective supporting shafts by rolling with respect to these. It is supposed to do.
[0033]
Thus, when the input shaft 3 is rotationally driven by transmission from an engine (not shown), this rotation is transmitted to the sun roller 50 via the one-way clutch 20, and the sun roller 50 rotates around the axis. The planetary rollers 51, 51... Which are in rolling contact with the outer periphery thereof rotate to revolve these carriages 53, and the rotor shaft 2 and the rotor 10 are rotationally driven at this revolution speed. At this time, the rotation of the input shaft 3 is decelerated and transmitted to the rotor shaft 2, and the rotor shaft 2 and the rotor 10 are driven at a lower speed than the rotational speed of the input shaft 3.
[0034]
On the other hand, a disc-shaped clutch plate 60 is integrally attached to the tip of the support shaft of each planetary roller 51, 51... Projecting from the carriage 53, and is opposed to the clutch plate 60. The clutch clutch 61 constitutes the hydraulic clutch 6.
[0035]
The clutch piston 61 is engaged with a spline formed on the outer periphery of a midway portion of the input shaft 3 at the inner diameter side thereof, and is attached to the input shaft 3 so that its rotation is restricted and movable in the axial length direction. A coil spring 63 is interposed between the coil receiver 63 and a spring receiver 62 engaged with the tip of the input shaft 3 on the side facing the plate 60, and is attached in a direction away from the clutch plate 60 by the spring force of the coil spring 63. It is energized.
[0036]
  The clutch piston 61 mounted in this manner includes a small diameter portion 61a that is coaxially provided on the non-opposing side of the clutch plate 60, and the outer diameter side of the clutch piston 61 is a transmission housing that constitutes the transmission chamber 4. 19 and the small-diameter portion 61a are fitted in fitting holes provided continuously on the same side of the transmission chamber 4 via separate seal rings 64 and 65, respectively. And a cylinder chamber 66 that is liquid-tightly sealed on both sides by the seal rings 64 and 65.(See Figure 2)Is forming.
[0037]
The cylinder chamber 66 communicates with the discharge chamber 18 of the pump body 1 through an oil guide passage 67 formed in the transmission housing 19 and the pump housing 14, and the other side of the clutch plate 60 is formed in the pump housing 14. A reflux oil passage 68 is provided to communicate with the suction oil passage 16 of the pump body 1. As a result, the hydraulic pressure generated in the discharge chamber 18 due to the rotation of the rotor 10 inside the pump body 1 and supplied to the hydraulic actuator (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 is kept in a low pressure state by communication with the suction oil passage 16, so that the clutch piston 61 is directed toward the clutch plate 60 by the action of the hydraulic pressure supplied to the hydraulic actuator. The pressing force exceeds the spring force of the coil spring 63, moves toward the clutch plate 60, and is pressed against the clutch plate 60.
[0038]
FIG. 2 is an operation explanatory view of the hydraulic clutch 6 and shows 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 supports the planetary rollers 51, 51. Because of being integrally attached to the tip of the shaft, the carriage 53 of the planetary rollers 51, 51... And the rotor shaft 2 holding the same 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, but this rotation is interposed between the input shaft 3 and the sun roller 50. It is allowed by the direction clutch 20 and does not hinder the rotation of the input shaft 3 and the rotor shaft 2.
[0039]
  As described above, the hydraulic clutch 6 is connected to the planetary roller by the action of the hydraulic pressure introduced into the cylinder chamber 66.Reducer and one-way clutch 20 WithSpeed change means 5To the constant speed position where the rotor shaft 2 rotates at the same speed as the input shaft 3.Performs switching operation. This switchingActionIs generated on the discharge side by the operation of the pump body 1 and the hydraulic pressure introduced into the cylinder chamber 66 isBy becoming higherDone.
[0040]
  The hydraulic pressure generated on the discharge side of the pump body 1 changes according to the operating state of the hydraulic actuator that is the supply destination thereof. For example, a hydraulic power steering system that assists the force necessary for steering an automobile with the hydraulic pressure. In the apparatus, the hydraulic pressure supplied to the apparatus increases with steering. When the hydraulic pump for automobiles according to the present invention is used, the clutch piston 61 is moved and pressed against the clutch plate 60 by the action of the supply hydraulic pressure that rises as described above.Constant speed positionAs a result, the rotational speeds of the rotor shaft 2 and the rotor 10 are increased, and the generated hydraulic pressure on the discharge side of the pump body 1 is further increased. Can be done.
[0041]
On the other hand, when the hydraulic pressure supplied to the power steering apparatus decreases with 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 is separated from the clutch plate 60 as shown in FIG. . At this time, the rotation of the input shaft 3 is transmitted to the rotor shaft 2 and the rotor 10 after being decelerated by the speed change 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 drive source is greatly reduced. can do.
[0042]
Further, as shown in FIG. 2, the clutch piston 61 is formed with a through hole 70 having one end opened inside the cylinder chamber 66 and penetrating in the axial direction, and a spool communicating with the middle portion of the through hole 70. The chamber 71 is formed as a circular hole drilled in the radial direction from the outer peripheral surface, and the centrifugal spool 7 is accommodated in the spool chamber 71.
[0043]
FIG. 3 is an enlarged cross-sectional view of the vicinity of the spool chamber 71 for explaining the operation of the centrifugal spool 7. As shown in the drawing, a centrifugal spool 7 is accommodated in the spool chamber 71 so as to be slidable in the depth direction thereof, that is, to be movable in the radial direction of the clutch piston 61. The open end of the spool chamber 71 toward the outer diameter side of the clutch piston 61 is liquid-tightly sealed by a lid member 72 screwed into the spool chamber 71, and the centrifugal spool 7 is interposed between the lid member 72 and the lid member 72. The spring force of the mounted coil spring 73 is biased inwardly of the spool chamber 71, that is, inward in the radial direction of the clutch piston 61.
[0044]
The spool chamber 71 for storing the centrifugal spool 7 is communicated with the inner peripheral side of the clutch piston 61 through a communication hole 74 formed radially inward from the bottom thereof, and is substantially equal in pressure to the arrangement chamber of the transmission means 5. It is kept. Further, the centrifugal spool 7 is formed with a communication hole 75 penetrating the axial center portion thereof, and communicates with the space on both sides of the centrifugal spool 7 inside the spool chamber 71. The sliding occurs without being affected by the pressure difference between the two sides.
[0045]
As described above, 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 indicated by white arrows in the figure. Since the acting direction is outward in the radial direction of the clutch piston 61, that is, opposite to the acting direction of the spring force of the coil spring 73, the centrifugal spool 7 responds to the force balance between the centrifugal force and the spring force. Slide.
[0046]
When the rotational speed of the input shaft 3 is low and the centrifugal force acting on the centrifugal spool 7 is less than the spring force of the coil spring 73, the centrifugal spool 7 is restrained to a position where it abuts against the bottom of the spool chamber 71, as shown in FIG. As shown in a), the through hole 70 intersecting the spool chamber 71 is blocked.
[0047]
On the other hand, when the rotational 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 fixed amount is exceeded, as shown in FIG. 3 (b), the through hole 70 intersecting the middle of the spool chamber 71 is opened, and the cylinder chamber 66 formed on one side of the clutch piston 61 is connected to the other side, that is, Thus, the transmission chamber 4 communicates with the space in which the transmission means 5 is disposed.
[0048]
FIG. 2 shows the operating state of the hydraulic clutch 6 when the rotational speed of the input shaft 3 is low and the centrifugal spool 7 is in the position shown in FIG. FIG. 4 is an explanatory diagram of the operation of the hydraulic clutch 6 in a state where the rotational speed of the input shaft 3 is high and the centrifugal spool 7 is moved to the position shown in FIG. .
[0049]
  When the centrifugal spool 7 is in the position shown in FIG. 3 (b), the through hole 70 is opened. As a result, the disposing space of the transmission means 5 communicating with the cylinder chamber 66 by this opening is as described above. If the suction oil passage 16 of the main body 1 communicates with the recirculation oil passage 68 and is kept in a low pressure state, and the sliding position of the centrifugal spool 7 is in the state shown in the drawing, it is introduced into the cylinder chamber 66 as described above. The hydraulic pressure is released to the space where 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 reflux oil passage 68. Accordingly, the internal pressure of the cylinder chamber 66 does not change regardless of the supply hydraulic pressure generated on the discharge side of the pump body 1, and the movement of the clutch piston 61 due to the action of the internal pressure does not occur.Speed changeMeans 5etcAs a result, the rotor shaft 2 and the rotor 10 are driven at a speed lower than the rotational speed of the input shaft 3.
[0050]
  As described above, when the rotational speed of the input shaft 3 driven by the engine becomes excessive, the centrifugal spool 7 moves by the action of centrifugal force accompanying this rotation, and releases the working pressure to the hydraulic clutch 6, Of the speed change means 5etcThe operation for prohibiting the switching to the high speed side is performed. As a result, the rotational speed of the rotor shaft 2 and the rotor 10 does not increase excessively with the increase of the rotational speed of the input shaft 3, and Unnecessary engine power loss can be reduced. In this state, since the rotational speed of the input shaft 3 is high,Speed changeThe rotational speed of the rotor 10 driven through the deceleration by the means 5 is sufficiently secured, and there is no possibility that the operation of the hydraulic actuator by the supply oil from the pump body 1 is impaired.
[0051]
In the above embodiment, the case where the pump body 1 is a vane pump has been described, but it is needless to say that another type of pump body 1 such as a gear pump or a trochoid pump may be provided.
[0052]
Further, as the speed change means 5, various types of transmissions capable of switching between two steps of high and low can be used. By using the planetary roller transmission or the planetary gear transmission shown in this embodiment, the switching can be performed. The hydraulic clutch 6 that operates can be compactly configured on one side of the pump body 1.
[0053]
FIGS. 5 and 6 are enlarged cross-sectional views showing a main part of a second embodiment of the automotive hydraulic pump according to the present invention. These drawings show the speed change means 5 and the hydraulic clutch 6 formed at the abutting portion between 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 of the first embodiment are denoted by the same reference numerals.
[0054]
  The speed change means 5 in this figure includes a planetary gear provided with a sun gear 50a, planetary gears 51a, 51a, ... and a fixed gear 52a.Equipped with reducering. The sun gear 50a is a disk-shaped external gear in which teeth that can be engaged with the planetary gear 51a are formed on the entire outer circumference of the sun gear 50a. Thus, the rotor shaft 2 and the input shaft 3 are supported between the butted ends so as to be rotatable coaxially therewith. As in the first embodiment, the one-way clutch 20 is interposed in the support portion of the sun gear 50a on the input shaft 3 side, and is configured to allow prior rotation of the sun gear 50a with respect to the input shaft 3. .
[0055]
The fixed gear 52a is an annular internal gear having teeth that can mesh with the planetary gear 51a on the entire inner circumferential surface, and is substantially aligned with the arrangement position of the sun gear 50a in the axial length direction. It is fitted and fixed inside the pump housing 14. The planetary gears 51a, 51a,... Are rotatably attached to one surface of a disk-shaped carriage 53 that rotates together with the rotor shaft 2 by separate support shafts, and are arranged on the outer periphery of the sun gear 50a and the inner periphery of the fixed gear 52a. Each tooth is meshed.
[0056]
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 the planetary gears 51a, 51a that are in rolling contact with the outer periphery of the sun gear 50a according to the rotation of the sun gear 50a. ... rotates and rolls along the inner periphery of the fixed gear 52a. Accordingly, the carriage 53 of the planetary gears 51a, 51a ... revolves, and the rotor shaft 2 and the rotor 10 rotate at this revolution speed. Driven. At this time, the rotational speeds of the rotor shaft 2 and the rotor 10 are sufficiently lower than the rotational speed of the input shaft 3.
[0057]
Further, the hydraulic clutch 6 is collectively supported at the tip ends of the support shafts of the planetary gears 51a, 51a... And the clutch plate 60 that rotates integrally with the carriage 53 and the rotor shaft 2, and the input shaft 3 so as to face this. And a clutch piston 61 that is constrained to rotate and is movably mounted in the axial direction. The clutch piston 61 is biased in a direction away from the clutch plate 60 by a plate spring 63a interposed between the clutch piston 61 and a spring receiver 62 engaged with the input shaft 3.
[0058]
The clutch piston 61 mounted in this way is projected coaxially on the non-opposing side with respect to the clutch plate 60, and is fitted via a seal ring 64 into a fitting hole continuously provided on the same side of the transmission housing 19. The small-diameter portion 61a is provided, and a seal ring 65 is interposed in a fitting portion between the small-diameter portion 61a and the input shaft 3. Thus, a liquid tightly sealed cylinder chamber 66 is formed between the oil seal 8 that seals the protruding portion of the input shaft 3 from the transmission housing 19 and the end surface of the small diameter portion 61a. .
[0059]
As in the first embodiment, the cylinder chamber 66 communicates with the discharge side of the pump body (not shown) by an oil guide passage 67 formed in the transmission housing 19 and the pump housing 14. A hydraulic pressure that is generated inside the pump body according to the rotation 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.
[0060]
Also, on the other side of the clutch piston 61, a hollow disc-shaped clutch plate 61b is attached so as to face the outer peripheral side of the clutch plate 60, and the clutch is resisted against the bias of the plate spring 63a. When the piston 61 moves, it comes into sliding contact with the clutch plate 60. Since the clutch plate 61b is configured separately from the clutch piston 61 in this way, the material of the clutch plate 61b can be freely selected, and the degree of friction associated with the sliding contact with the clutch plate 60 is set appropriately. It becomes possible to do.
[0061]
  The other side of the clutch piston 61 facesSpeed changeThe disposition chamber of the means 5 is communicated to the suction side of the 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 is kept in a low pressure state. 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 plate spring 63a and moves toward the clutch plate 60. As shown in FIG. 5, it is pressed against the clutch plate 60 via the clutch plate 61b.
[0062]
At this time, the carriage 53 of the planetary 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, and supports the carriage 53. The rotor shaft 2 rotates at the same speed as the input shaft 3. At this time, the sun gear 50a rotates at a high speed in accordance with the rotation of the planetary gears 51a, 51a... Meshed with the external teeth of the sun gear 50a, but this rotation is caused by the one-way clutch 20 interposed between the input shaft 3 and the sun gear 50a. It is allowed and does not hinder the integral rotation of the input shaft 3 and the rotor shaft 2.
[0063]
  As described above, the hydraulic clutch 6 is operated by the internal pressure of the cylinder chamber 66,Planetary gear reducer and one-way clutch 20 WithSpeed change means 5To the constant speed position where the rotor shaft 2 rotates at the same speed as the input shaft 3.Performs switching operation. As in the first embodiment, the internal pressure of the cylinder chamber 66 changes according to the operating state of the hydraulic actuator that is the delivery destination of the discharge pressure of the pump body, is high during operation, and is not operating Becomes lower. Therefore, the transmission means 5Constant speed positionIs switched only during the operation of the hydraulic actuator. During this operation, the rotor shaft 2 rotates at a high speed, and as a result, a sufficient amount of high-pressure hydraulic oil is supplied, so that the hydraulic actuator While the operation can be surely performed, while the hydraulic actuator is not operating, the rotor shaft 2 rotates at a low speed. As a result, the power load of the engine serving as the drive source can be greatly reduced.
[0064]
The clutch piston 61 that performs the above operation is formed with a spool chamber 71 as a circular hole penetrating in the radial direction from the outer peripheral surface, and the spool chamber 71 houses a centrifugal spool 7a. The clutch piston 61 has a first throttle hole 70a that communicates the spool chamber 71 with the cylinder chamber 66, and a second throttle hole 70b that communicates with the disposing chamber of the transmission means 5 on the outer side in the radial direction. Are formed in the axial direction.
[0065]
FIG. 7 is an enlarged cross-sectional view of the vicinity of the spool chamber 71 for explaining the operation of the centrifugal spool 7a. As shown in the figure, the spool chamber 71 has an opening end on the outer diameter side of the clutch piston 61 sealed in a liquid-tight manner by a lid member 72 screwed thereto, and the opening end on the other side is closed by the outer periphery of the input shaft 3. It consists of The centrifugal spool 7a has two land portions slidably fitted in the spool chamber 71 on both sides in the axial length direction, and these are connected by a small diameter portion. The spring force of the coil spring 73 interposed therebetween is biased toward the inside of the spool chamber 71, and the clutch piston 61 can move in the radial direction against this bias.
[0066]
The land portions on both sides of the centrifugal spool 7a are set so that the distance between the respective facing surfaces substantially corresponds to the distance between the opening positions of the first and second throttle holes 70a, 70b in the spool chamber 71. Control edges 71a and 71b are formed by chamfering the entire circumference at the opposing edges of the land portions. Further, both sides of the centrifugal spool 7a inside the spool chamber 71 are communicated with the transmission means 5 on the side where the transmission means 5 is arranged by a communication hole 74a penetrating the shaft center portion of the lid member 72 and the input shaft 3, respectively. 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 between the two sides.
[0067]
As described above, the centrifugal spool 7a accommodated in the spool chamber 71 has a radial outward direction as indicated by white arrows in the drawing according to the rotation of the clutch piston 61 accompanying the rotation of the input shaft 3. That is, a centrifugal force acts in the direction opposite to the direction of the spring force of the coil spring 73, and the centrifugal spool 7a slides according to the force balance between the centrifugal force and the spring force.
[0068]
When the rotational speed of the input shaft 3 is low and the centrifugal force acting on the centrifugal spool 7a is less than the spring force of the coil spring 73, the centrifugal spool 7a is formed on the bottom surface of the spool chamber 71 as shown in FIG. It is in the position which contact | abutted to the outer peripheral surface of the input shaft 3 used. 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 to the outside of the outer land portion. The internal pressure of the cylinder chamber 66 is the spool chamber 71. Stop inside. At this time, the transmission means 5 is switched by the operation of the hydraulic clutch 6 as described above, and the rotational speed of the rotor shaft 2 changes between high and low.
[0069]
On the other hand, when the rotational 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 radially outward, and this sliding amount becomes a predetermined amount. When it reaches, as shown in FIG. 7 (b), the second throttle hole 70 b opens to the inside of the outer land portion, and the cylinder chamber 66 communicates with the installation space of the transmission means 5. As a result, the internal pressure of the cylinder chamber 66 is released to the disposition chamber of the transmission means 5 through the first and second throttle holes 70a and 70b, and further, as shown in FIG. Released on the suction side.
[0070]
  Therefore, 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 due to the action of this internal pressure does not occur.Speed changeMeans 5Constant speed positionAs a result, the rotor shaft 2 is driven at a speed lower than the rotational speed of the input shaft 3.
[0071]
  As described above, the centrifugal spool 7a releases the working pressure applied to the hydraulic clutch 6 when the rotational speed of the input shaft 3 exceeds a predetermined amount, similarly to the centrifugal spool 7 in the first embodiment.etcSwitching to the high speed side is prohibited, and it acts to reduce unnecessary power loss of the engine during high-speed driving.
[0072]
Furthermore, in the second embodiment, the working pressure is released according to the movement of the centrifugal spool 7a through a release oil passage including first and second throttle holes 70a and 70b and a fixed throttle 68a. It has become. As a result, the release of the working pressure gradually occurs with the flow resistance when pressure oil flows through the first and second throttle holes 70a and 70b as the variable throttles and the fixed throttle 68a. The switching operation of No. 6 is not performed rapidly, discontinuity of the pressure characteristic on the discharge side of the hydraulic pump is eliminated, and a smooth pressure characteristic is obtained. In addition, the change mode of the throttle area in the first and second throttle holes 70a and 70b can be freely changed by changing the shape of the control edges 71a and 71b formed as described above in the land portion of the centrifugal spool 7a. The generation timing and operation speed of the switching operation can be adjusted, and a desired pressure characteristic can be easily realized.
[0073]
【The invention's effect】
  As described in detail above, in the automotive hydraulic pump according to the present invention, the input shaft connected to the output end of the engine is connected between the rotor and the rotor.Turn intoThe speed means is arranged and the speed change meansTo constant speed positionSince the hydraulic clutch that performs the switching operation by the action of the supply hydraulic pressure generated by the rotation of the rotor is provided, the shift according to the operation state of the hydraulic actuator that is the supply destination is the sensor for detecting the operation state, and this detection When the hydraulic actuator that does not need to supply hydraulic pressure can be operated without the need for control means according to the results, the rotational speed of the rotor decreases to reduce the power loss of the engine as the drive source, and the hydraulic pressure During the operation of the operating device, the rotational speed of the rotor can be increased to ensure a sufficient supply hydraulic pressure.
[0074]
  In addition, since it has a centrifugal spool that moves by the action of the centrifugal force accompanying the rotation of the input shaft and releases the working pressure to the hydraulic clutch, a shift according to the rotational speed of the engine that is the drive source is used for detecting the rotational speed. This is realized without the need for a sensor and a control means corresponding to the detection result.etcSwitching to the high speed side is not performed, and unnecessary power loss of the engine due to excessive increase in the rotational speed of the rotor can be further reduced.
[0075]
In addition, since the variable pressure passage and the fixed throttle are provided in the oil release passage for the working pressure to the hydraulic clutch, the change of the working pressure to the hydraulic clutch with the movement of the centrifugal spool becomes gradual, and the switching operation of the hydraulic clutch is performed rapidly. In addition, the discontinuity of the pressure characteristic on the discharge side of the hydraulic pump is eliminated, and the adjustment of the pressure characteristic can be easily performed by processing the control edge provided on the centrifugal spool and the fixed throttle, thereby obtaining a desired pressure characteristic. It becomes possible.
[0076]
Furthermore, since the speed change means is constituted by a planetary transmission, it can be compactly formed on one side of the pump body together with a hydraulic clutch for changing the gear ratio, and the above-described effects lead to an increase in the overall structure. The present invention has an excellent effect that it can be realized without any problems.
[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 operation explanatory diagram of a hydraulic clutch.
FIG. 3 is an enlarged cross-sectional view of the vicinity of a spool chamber for explaining the operation of the centrifugal spool.
FIG. 4 is an operation explanatory view of a hydraulic clutch when the centrifugal spool is moved.
FIG. 5 is an enlarged cross-sectional view showing a main part of a second embodiment of the automotive hydraulic pump according to the present invention.
FIG. 6 is an enlarged cross-sectional view of a main part showing a second embodiment of the automotive hydraulic pump according to the present invention.
FIG. 7 is an enlarged cross-sectional view of the vicinity of a spool chamber for explaining the operation of a centrifugal spool according to a second embodiment.
[Explanation of symbols]
1 Pump body
2 Rotor shaft
3 Input shaft
5 Shifting means
6 Hydraulic clutch
7 Centrifugal spool
7a Centrifugal spool
10 Rotor
14 Pump housing
19 Transmission housing
20 one-way clutch
50 sun rollers
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 aperture
70 Through hole
70a First aperture
70b Second aperture
71 Spool chamber
71a Control edge
71b Control edge
73 Coil spring

Claims (4)

An automotive hydraulic pump that includes a rotor that rotates by transmission from an input shaft that is interlocked and connected to an output end of an engine, and that generates hydraulic pressure supplied to a hydraulic actuator mounted on the vehicle, wherein the input shaft and the rotor A speed change means for switching a speed ratio between the two to a constant speed position where the rotation of the input shaft is transmitted to the rotor at a constant speed and a speed reduction position where the rotation of the input shaft is transmitted to the rotor at a reduced speed. And a hydraulic clutch that causes the transmission means to switch to the constant speed position by the action of the supply hydraulic pressure that rises in accordance with the operation of the hydraulic actuator. . The automobile hydraulic pump according to claim 1, further comprising a centrifugal spool that is moved by the action of a centrifugal force accompanying the rotation of the input shaft, releases an action pressure to the hydraulic clutch, and prohibits a switching operation to the constant speed position . . The working pressure release oil path includes a variable throttle that changes a throttle area by a control edge formed in a part of the centrifugal spool, and a fixed throttle that adds a predetermined throttle resistance to the pressure oil that has passed through the variable throttle. The automobile hydraulic pump according to claim 2 provided.   The speed change means is arranged coaxially between the planetary body held by a carriage that rotates integrally with the rotation shaft of the rotor, and between the rotation shaft and the input shaft. A solar disk that makes rolling contact, and a one-way clutch that is interposed between the solar disk and the input shaft, and that allows a preceding rotation of the solar disk, and the hydraulic clutch rotates integrally with the carriage The clutch plate which carries out a rotation and is restrained by the said input shaft, The piston which moves to an axial length direction by the effect | action of the said supply hydraulic pressure, and is pressed against the said clutch plate is provided in any one of Claim 1 thru | or 3 Hydraulic pump for automobiles.

Images