JPS6218B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a controller for an all-hydraulic power steering system that eliminates the need for mechanical linkages.

Conventionally, this type of device was
The device described in this issue has been well known for a long time. This controller employs a rotary valve as a control valve, and has many intersecting holes, circumferential grooves, axial grooves, and through holes in the housing, sleeve, and spool. Since these grooves and holes are rotary valves, accurate angle indexing is required, and since they are drilled or milled, it is difficult to process them efficiently. In addition, since oil-tightness between components is required, including the housing into which the sleeve fits, each mating surface requires high-precision machining to provide oil-tightness and clearance for smooth rotation.
Moreover, each member is long in the axial direction, making it difficult to process. Furthermore, since the input shaft is pivotally supported by a spool, there is a drawback in that a steering column, which is not described in the publication, must actually be provided to receive the radial load of the input shaft. As a device that solves the drawbacks of rotary valves, there is known a controller that uses a slide valve and is described in Japanese Patent Publication No. 49-23171. However, since this device moves and rotates the spool in the axial direction, the structure of the coupling device between the spool and the input shaft and the coupling device between the trochoid pump and the spool are complicated, and in addition, they are installed inside the spool. The disadvantage is that the diameter of the spool valve has become larger. Furthermore, since the rectifier valve is rotated at the revolution speed of the trochoid pump, there are drawbacks such as the structure of the rectifier valve being complicated and a driving means for the same being required. Unexamined Japanese Patent Publication No. 1973-1987 as a controller that uses a slide valve that does not involve rotation.
There is a device described in Publication No. 82031, but in this device, a set of planetary gears is connected to the input shaft, the internal gear or the planetary gear moves the control valve, and the center gear is connected to the inner rotating member of the trochoid pump. It is connected. Therefore, if the pump fails,
The trochoid pump will be driven via a planetary gear system, which must be designed as a strength member. For this reason, the planetary gear device becomes large, and the controller also becomes large.
Further, since the mechanism for doubling the discharge amount per revolution of the input shaft relies on the speed increasing ratio of the planetary gear device, a large doubling rate cannot be obtained. Since the control valve spool requires a centering spring, the area around the fully hydraulic control valve, which is already large, becomes even larger. Since the centering spring and the driving pin are attached to one end of the spool, and the spring is driven on one side, there are also drawbacks such as poor balance.

The applicant has aimed to eliminate the above-mentioned drawbacks by creating a compact, well-balanced hydraulic system, easy valve processing, easy adaptation to the presence or absence of a separate circuit other than steering, and an input shaft. With the aim of providing a controller to which a handle, etc. can be directly attached without the need for a handle column, we proposed a controller in Japanese Patent Application Laid-open No. 54-113129 (Japanese Patent Application No. 1975-1975), but the control Since the valve is composed of a slide-type spool valve, the control valve itself is simple and easy to process, and the diameter of the control valve is mostly determined by the flow rate of the fluid to be controlled by the control valve, so there are no other restrictions, so the control valve itself is simple and easy to process. Although the diameter size of the control valve can be selected, the longitudinal dimension of the control valve increases due to the increased switching function of the control valve.
For this reason, the minimum diameter dimension makes it difficult to accurately and efficiently process holes or annular grooves on the housing side.

Furthermore, since the longitudinal direction of the control valve is disposed perpendicular to the axis of the controller, there is a drawback that the width of the controller increases.

The object of the present invention is to provide a controller that eliminates the above-mentioned drawbacks.

The configuration of the present invention that achieves the above object includes an input shaft connected to a handle of a vehicle, a cover member that fixes the input shaft in the axial direction via a bearing and rotatably supports the input shaft, and the cover member at one end. and a measuring instrument fixed to the other end thereof, a slide type control valve provided in the housing, and an outer valve member press-fitted and fixed to an inner cylindrical surface parallel to the input shaft in the housing. a rectifying valve provided adjacent to the meter; an oil inlet from a hydraulic source provided in the housing so as to communicate with the control valve; a first oil outlet communicating with an oil tank; and a second oil outlet communicating with a steering actuator. a second oil outlet communicating with a separate oil inlet/outlet and a separate circuit; an oil passage provided in the housing that connects the control valve and the rectifier valve; 1 planetary gear device, and a center gear integrally formed with a center gear of the first planetary gear device, and the rotation of the inner valve member of the rectifier valve is controlled via the first planetary gear device. a second planetary gear device that transmits the transmission to the valve; and a drive shaft that rotates following the rotation of the control input shaft above a certain limit and transmits the rotation of the inner member of the meter to the inner valve member of the rectifier valve. , a controller for a fully hydraulic power steering device comprising the input shaft and a torsion bar having both ends fixed to the drive shaft, wherein the control valves include two control valves provided in the housing parallel to the input shaft. spools are fitted oil-tightly into the respective cylindrical holes, and when the two spools are engaged with the internal gear of the first planetary gear unit and the internal gear rotates, the rotation The all-hydraulic power steering device controller is characterized in that it has a connecting device that connects the internal gear and the two spools, which are interlocked in opposite directions by motion.

To explain the embodiment shown in the figure, the outline of the all-hydraulic power steering system including the controller 40 is as shown in FIG. 1, as shown in FIG. It consists of a separate fluid circuit 43, consisting of an oil inlet 44 from a hydraulic source in the controller, a first oil outlet 45 leading to an oil tank, and two oil outlets 46, 47 leading to the steering actuator. and a second oil outlet 48 communicating with another circuit via a pipe line. The controller 40 is operated by a handle 41, which is fixed to the shaft end 13 of the input shaft 12 shown in FIG. The input shaft 12 is a hollow shaft having a flange-shaped carrier 11 of a first planetary gear set, which will be described later, and is rotatably supported by the cover member 15 by two ball bearings 101 and 102. The opposing sides of the outer rings of the two ball bearings 101 and 102 are in contact with the stepped portion of the cover member 15, and the opposite side surfaces of the inner rings are fixed to the stepped portion of the input shaft 12 and the input shaft 12. Since the input shaft 12 is in contact with the retaining ring 103, the input shaft 12 is fixed in the axial direction.
It is held within the bearing gap which is also preloaded in the circumferential direction. An oil seal 104 is installed between the two ball bearings 101 and 102. Cover member 15
is fitted into the inner cylindrical hole 20 of the housing 14 of the controller, and is fixed with a bolt 105 with the flange in contact with one end surface of the housing 14. Housing 1
A measuring instrument 5 is fixed to the other end of 4 with a bolt 106. The meter 5 consists of an outer member 7 of the trochoid pump, a partition plate 38, a lid plate 39, and an inner member 6, and the parts other than the inner member 6 are fixed to the housing 14 with the bolts 106. Housing 14
There is an inner cylindrical surface parallel to the input shaft 12 inside.
A rectifier valve 8 is provided adjacent to the meter 5 here. The rectifier valve consists of an outer valve member 28 and an inner valve member 29 fitted to the inner surface of the outer member 28. The outer valve part 28 has a circumferential groove 73 on the inner surface on the measuring instrument 5 side, and an axial groove on the outer circumferential surface. 97, hole 98 connecting these two,
Seven chambers 90, 91, 92, 9 formed between the teeth of the outer member 7 and inner member 6 of the measuring instrument shown in FIG.
Passages 83, 84, 85, 86, 8 indicated by dotted lines opening at 3, 94, 95, 96, respectively
7, 88, 89, seven holes 76, 77, 78, 79, 8 arranged radially orthogonally to this passage.
0, 81, 82 and one through hole (not shown) communicating with the circumferential groove 72 provided on the outer peripheral surface of the inner valve member 29. Said passages 83, 84, 8
5, 86, 87, 88, and 89 are circular holes formed by semicircular axial grooves provided on the outer peripheral surface of the outer valve member 28 and grooves similarly provided in the housing 14, and are formed into circular holes in the partition plate 38 of the measuring instrument. It is formed by connecting to the provided hole. After the outer valve member 28 is processed in this manner, it is press-fitted and fixed to the inner cylindrical surface of the housing 14.
The outer surface of the inner valve member 29 has a circumferential groove 72 provided at a position near the input shaft on the outer circumferential surface, and seven radial holes 76, 77, 78 between the circumferential groove 72 and the outer valve member.
79, 80, 81, 82, and six axial grooves 75 provided in the middle of the grooves 74 to connect the holes and the circumferential groove 73. (See Figures 2 and 4). Further, the inner valve member 29 has a flange-shaped carrier 26 of a second planetary gear device, which will be described later, near the input shaft, and a hole 31 into which a pin 30 is fitted without a gap. As shown in FIGS. 2 and 5, the pin 30 is inserted into a groove 33 provided at the shaft end of the input shaft 12 with a predetermined gap, and is also inserted into a groove 32 provided at the shaft end of the drive shaft 9, which will be described later. It is inserted without any gap in the circumferential direction. The shaft end of the input shaft 12 provided with the groove 33 fits into the inner surface of the inner valve member 29 with a sufficient clearance, and is fitted onto the outer circumferential surface of the input shaft between the end surface of the inner valve member 29 and the carrier 11 of the input shaft. The center gears 19 and 23 of the first and second planetary gear devices integrally formed are rotatably fitted with a gap. The first planetary gear device includes a central gear 19, several planetary gears 16 mounted on the carrier 11 with a pin 17 so as to be rotatable around the pin, and an inner gear rotatably fitted in an inner cylindrical hole 20 of the housing. A notch 21 is provided on the outer periphery of the internal gear 18, and a notch 21 is provided on the outer periphery of the internal gear 18.
A driving pin 22 is implanted in a direction changing member 121 which is swingably attached to the bottom surface of the drive pin 120 with a pin 120.
The rotation of the internal gear 18 is caused by the direction changing member 1
21 is adapted to swing around the pin 120. The second planetary gear device is the center gear 23
, several planetary gears 24 mounted by pins 27 on a carrier 26 of the inner valve member, and an internal gear 25 fixed in an inner cylindrical bore 20 of the housing. In FIG. 5, the input shaft 12 and pin 30
Since there is a gap between the input shaft 12 and the input shaft 12, the inner valve member 29 of the rectifier valve and the drive shaft 9 rotate via the pin 30 only after the input shaft 12 rotates beyond a certain limit. The end 37 of the drive shaft 9 on the side opposite to the input shaft is provided with teeth that mesh with teeth provided on the inner surface of the inner member 6 of the meter, and rotates the inner member 6 to the inner valve member 29 of the rectifier valve. Furthermore, when the hydraulic pressure is not working, the rotation of the input shaft 12 can be transmitted to the internal member 6 of the meter so that it can act as a pump. A second groove 34 perpendicular to the groove 32 is provided at the input shaft side end of the drive shaft 9, into which a torsion bar pin 35 implanted at one end of the torsion bar 10 is inserted without any gap. ing. The other end of the torsion bar 10 is fixed to the input shaft 12 with a pin 36. As shown in FIG. 6, the control valve 2 has two large diameter holes 12 in the housing 14 parallel to the input shaft 12.
2A and 122B, and a large diameter hole 122 in the back
A, 122B are connected to two cylindrical holes 68A,
68B is provided parallel to the input shaft 12, and two spools 1A, 1B are arranged to fit oil-tightly into the cylindrical holes 68A, 68B, respectively, and relief holes 123A, 123B for machining are provided at the innermost part. is provided. A first oil outlet 45 is provided in the middle of the two large diameter holes 122A, 122B and is perpendicular thereto, and the direction changing member 121 is attached to the bottom of the first oil outlet 45 with a pin 120. There is further a circular hole 124 at the bottom, into which the driving pin 22 is fitted with a large gap, and the driving pin 22 can swing around the pin 120 within the diameter of the circular hole 124.
The direction changing member 121 has a wire on both sides of the pin 120 in the direction perpendicular to the line connecting the pin 120 and the driving pin 22.
Spool drive pins 125A and 125B that engage with notches provided in the spools 1A and 1B are implanted, and these drive pins 22 and the direction changing member 1
21, pin 120, spool drive pin 125A,
125B is the internal gear 18 of the first planetary gear device.
When the controller rotates, the movement of the drive pin 22, which is displaced in a direction perpendicular to the axial direction of the input shaft 12 of the controller, is controlled by the direction changing member 121 about the pin 120.
, and the spool drive pin 12
2 spools 1A, 1 by 5A, 125B
The internal gear 18 and the spools 1A, 1B of the first planetary gear system for directly moving the gears B in opposite directions.
It constitutes a connecting device that connects the two. A lid, which forms one side of the notch in which the spool drive pins 125A, 125B are engaged, is fixed with a bolt to the end of the two spools 1A, 1B on the direction changing member 121 side. Part is spool 1A, 1
Large-diameter cylindrical holes 53A and 53B are connected to center holes 55A and 55B provided in B, and a spring 52 is in pressure contact with the stepped portion of the center hole and the cylindrical hole, and the direction is changed between the spools 1A and 1B. The members 121 are connected without any gaps. The two cylindrical holes 68A, 688B forming the sleeve part have inlet/outlet circumferential grooves 62, 6 communicating with the two oil outlets 46, 47.
3. Inlet circumferential grooves 57A, 57 leading to oil inlet 44
B, and an outlet circumferential groove 6 leading to the second oil outlet 48
1A and 61B are provided, and the inlet circumferential groove 57
A and 57B communicate with each other through a first connection hole 58, and outlet circumferential grooves 61A and 61B communicate with each other through a second connection hole 59. The spools 1A, 1B include inlet/outlet lands 108, 109 where the sleeve inlet/outlet circumferential grooves 62, 63 face each other in the illustrated neutral state, an inlet land 110 with the right side of the sleeve inlet circumferential grooves 57A, 57B closed and the left side open; 111, and an outlet circumferential groove 61A, which faces the outlet circumferential grooves 61A, 61B.
Exit land 112, 1 with only the right side of 61B open
13 are provided. In addition, entrance land 10
The right side of 8,109 has a cylindrical hole 6 with a smaller diameter than the land.
8A, 68B and the large diameter holes 122A, 122B leading to the first oil outlet 45, and are always a low pressure part, and through holes 60A, 60B connecting the center holes 55A, 55B and the low pressure part are provided here. It is being Note that the lands 66, 67 sandwiched between the sleeve entrance/exit grooves 62, 63 and the entrance circumferential grooves 57A, 57B
Oil passages 64 and 65 leading to the rectifier valve 8 are open, respectively, and one oil passage 64 passes through a through hole (not shown) provided in the outer valve member 28 of the rectifier valve.
A circumferential groove 7 provided closer to the input shaft of the inner valve member 29
2, and the other oil passage 65 is connected to an axial groove 97 of the outer valve member 28.

Next, the operation will be explained. In the neutral state, each member does not move as shown in the figure. The hydraulic oil enters from the oil inlet 44 of the controller and enters the inlet circumferential groove 57 of the control valve.
The entire amount flows from the second oil outlet 48 to the separate circuit 43 via the A, 57B outlet circumferential grooves 61A, 61B, and then returns to the oil tank 42. By providing holes 71 indicated by dotted lines in the lands 112 and 113 of the spool facing the outlet circumferential grooves 61A and 61B, the hydraulic oil does not flow into the separate circuit 43 and can flow through the large diameter cylindrical holes 53A and 53B and the through holes 60A and 60B. Since the oil returns to the oil tank 42 through the first oil outlet 45, the same controller can be used by providing the hole 71 in vehicles that do not require a separate circuit. For example, when the handle 41 is rotated clockwise, the meter 5 does not rotate at first, so the rectifying valve 8, the two central gears 19,
23 also does not rotate, and the carrier 1 is integrated with the input shaft 12.
1 rotates clockwise, and the planetary gear 16 of the first planetary gear device revolves clockwise around the center gear 19 and rotates clockwise. Therefore, the internal gear 18 also rotates clockwise, and the direction changing member 12
1 in the clockwise direction in FIG. Therefore, the spool 1A on the upper side of the figure is displaced to the right, and the spool 1B on the lower side of the figure is displaced to the left. At this time, the torsion bar 10 is twisted and applies a reaction force proportional to the twist angle to the input side. When the spools 1A and 1B are slightly displaced, the orifices a and i shown in Fig. 6 are squeezed together.
Or since it is closed, the inlet circumferential grooves 57A, 57
The pressure B increases depending on the load on the actuator 4 or the opening degree of the orifices a and i. At this time, the orifices h, d, and f open, so the hydraulic oil in the lower inlet circumferential groove 57B passes through the orifice h, passes through the oil passage 65 that opens into the land 67 adjacent to the inlet circumferential groove 57B, and passes through the rectifier valve 8. into the circumferential groove 73 on the inner surface of the outer valve member, the axial groove 75 in the inner valve member, the radial holes 80, 81 in the outer valve member shown in FIG.
82, the left chambers 94, 95, 96 of the measuring instrument 5 in FIG. 3 are expanded. The center of the inner member 6 of the scale thus begins to rotate counterclockwise around the center of the outer member 7, while the inner member 6 itself rotates clockwise. At the same time, the right chambers 91, 92, 93 contract, and the hydraulic oil in these chambers is pushed out, and the passages 84, 85 on the outer surface of the outer valve member,
radial holes 77, 78, 79 from 86, axial groove 74 of inner valve member, circumferential groove 72, outer valve member 28
The oil flows out from the upper land 66 through the through hole (not shown) in the housing and into the orifice d.
The oil is sent from the upper inlet/outlet circumferential groove 63 to the oil inlet/outlet 47 to the upper chamber of the actuator 4, and actuates the actuator 4. The hydraulic oil discharged from the lower chamber of the actuator 4 flows from the other oil inlet/outlet 46 to the lower inlet/outlet circumferential groove 62, passes through the orifice f, and is returned to the oil tank 42 from the low pressure section via the first oil outlet 45. . The rotation of the inner member 6 of the measuring instrument is
Since the inner valve member 29 of the rectifier valve is rotated clockwise by the drive shaft 9, the radial hole 7
6, 77, 78, 79, 80, 81, 82 are sequentially switched to the axial grooves 74, 75,
As long as the input shaft 12 is rotating, the inner member 6 of the meter continues to rotate. The rotation of the inner valve member 29 of the commutator valve is caused by the rotation of the inner valve member 29 of the rectifying valve.
Since the carrier 26 rotates clockwise, and the internal gear 25 is fixed, the planetary gear 24 rotates counterclockwise while revolving clockwise inside the internal gear 25. Therefore, since the center gear 23 rotates clockwise, its rotation is the first
Since the planetary gear 16 of the planetary gear device is driven to rotate counterclockwise, the rotation of the planetary gear 16 given by the handle 41 is canceled out or reversed. As the rotation by the handle 41 continues, the control valve 2 maintains a constant displacement proportional to the load and input speed, and the first planetary gear set and the second planetary gear set continue to rotate synchronously. If the input rotation is stopped, the rotation transmitted through the second planetary gear set will drive the planetary gear 16 counterclockwise, causing the internal gear 18 to rotate counterclockwise and the control valve 2 to the neutral position. By being returned, the flow of hydraulic oil to the meter 5 or actuator 4 is stopped. With such an operation, the actuator 4 always operates in proportion to the input rotation applied to the handle 41. In this manner, the flow of hydraulic oil to the separate circuit 43 is prioritized to flow to the actuator 4 during steering using the handle 41, and the remainder flows. In addition, regarding the operation of the steering device, it is almost irrelevant whether there is a load acting on the separate circuit 43, and depending on the presence or absence of the load,
The back pressure of the steering device itself does not increase.

With the controller of the present invention configured as described above, (a) an input device such as a steering wheel can be directly attached to the input shaft without requiring a steering column;

(b) In the event of a failure of the hydraulic drive source, the input shaft can operate the measuring instrument via the drive shaft.

(c) The rectifier valve can be made small and easy to process.

(d) The planetary gear device can be made smaller.

(E) When installed on a vehicle that has a separate circuit for work equipment, etc. in addition to the steering system, hydraulic oil can be flowed preferentially to the steering system, but when installed on a vehicle that does not require a separate circuit, This can be done simply by providing a hole in the spool that communicates with the inner surface.

In a controller that has the following effects, the control valve is divided into two parts and placed in the axial direction of the input shaft, so the hole into which the spool is fitted is short in the axial direction, and the spool diameter is set to the minimum. However, the inner diameter of the sleeve and the annular groove of the sleeve and spool can be machined with high precision and efficiency, and the width dimension perpendicular to the input axis of the controller can be reduced. Therefore, the controller has the effect of being made smaller in the axial, diametric and width directions as well. Furthermore, since the drive direction changing member that drives the control valve is placed inside the first oil outlet, there is no need to separate parts such as a lid or the housing for machining, allowing for compact and highly accurate control. This has the effect of providing the device at a low cost.

[Brief explanation of the drawing]

The drawings show embodiments of the present invention, in which Fig. 1 is a conceptual diagram of a power steering device, Fig. 2 is a vertical cross-sectional view of the controller, Fig. 3 is a cross-sectional view taken along the - line in Fig. 2, and Fig. 4 is a cross-sectional view of the controller.
The figure is a cross-sectional view taken along the - line in Fig. 2, Fig. 5 is a cross-sectional view taken along the - line in Fig. 2, and Fig. 6 is a cross-sectional view of the control valve, and a conceptual diagram showing how related equipment is connected to it. be. Explanation of symbols, 2: Control valve, 3: Hydraulic source, 4: Actuator, 5: Meter, 8: Rectifier valve, 9: Drive shaft, 10: Torsion bar, 12: Input shaft, 1
4: Housing, 15: Cover member, 19, 2
3: Center gear, 28: Outside valve member, 42: Oil tank, 43: Separate circuit, 44: Oil inlet, 45: First oil outlet, 46, 47: Oil inlet/outlet, 48: Second oil outlet, 64 , 65: Oil path, 101, 102: Ball bearing.

Claims (1)

[Scope of Claims] 1. An input shaft connected to a handle of a vehicle, a cover member that fixes the input shaft in the axial direction via a bearing and rotatably supports the input shaft, and has one end to which the cover member is fixed, and the other. A housing with a measuring instrument fixed at the end,
a slide type control valve provided in the housing; a rectifier valve provided adjacent to the meter with an outer valve member press-fitted and fixed to an inner cylindrical surface parallel to the input shaft in the housing; An oil inlet from a hydraulic source provided in the housing so as to communicate with the control valve, a first oil outlet that communicates with an oil tank, two oil inlets and outlets that communicate with a steering actuator, and a second oil outlet that communicates with a separate circuit. an oil passage provided in the housing that connects the control valve and the rectifier valve; a first planetary gear device that transmits rotation of the input shaft to the control valve; and the first planetary gear device. a second planetary gear set having a center gear integrally formed with a center gear for transmitting rotation of the inner valve member of the rectifier valve to the control valve via the first planetary gear set; and a control input; a drive shaft that rotates following the rotation of the shaft above a certain limit and transmits the rotation of the inner member of the measuring instrument to the inner valve member of the rectifier valve; and a drive shaft that has both ends fixed to the input shaft and the drive shaft, respectively. In the controller for a fully hydraulic power steering device including a torsion bar, the control valve includes two valves provided in the housing parallel to the input shaft.
spools that fit oil-tightly into the respective cylindrical holes, and when the two spools are engaged with the internal gear of the first planetary gear unit and the internal gear rotates, A controller for an all-hydraulic power steering system, comprising a connecting device that connects the internal gear and the two spools, which are rotated to interlock with each other in opposite directions. 2. The control valve controls the flow of hydraulic oil to the two oil inlets and outlets, and controls the remaining hydraulic oil to flow from the second oil outlet to a separate circuit. The controller for a fully hydraulic power steering device according to item 1. 3. The total hydraulic pressure according to claim 1, wherein the control valve can prevent the flow of hydraulic oil to the second oil outlet by providing a hole communicating with the inner surface of the spool in the low pressure section. Controller for power steering system.