KR960000598Y1 - Rotary valve for power steering system - Google Patents

Abstract

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Description

Rotary Valves in Power Steering

1 to 3 show a rotary valve of a power steering apparatus according to an embodiment of the present invention,

1 is an exploded view of the valve groove

2 degrees cross section

3 is an exploded view of the valve groove during valve operation.

4 is a view corresponding to FIG. 1 of the second embodiment.

5 is a view corresponding to FIG. 2 of the second embodiment.

6 is a view corresponding to FIG. 1 of the third embodiment.

7 is a view corresponding to FIG. 2 of the third embodiment.

8 is a view corresponding to FIG. 1 of the fourth embodiment.

9 is a view corresponding to FIG. 2 of the fourth embodiment.

10 is a view corresponding to FIG. 1 of the fifth embodiment.

11 is a view corresponding to FIG. 2 of the fifth embodiment.

12 is a view corresponding to FIG. 1 of the sixth embodiment.

13 is a view corresponding to FIG. 2 of the sixth embodiment.

14 is a view corresponding to FIG. 1 of a conventional rotary valve.

15 is a view corresponding to FIG. 2 of the conventional rotary valve.

16 is a view corresponding to FIG. 3 of the conventional rotary valve.

* Explanation of symbols for main parts of the drawings

(2): Valve rotor (4): Valve groove to pump

(6): Valve groove to tank (8): Valve sleeve

(10), (12): Valve grooves through the working chamber of the cylinder

(16): passage hole through the pump (18): passage hole through the tank

The present invention relates to a rotary valve of a power steering device.

The rotary valve of the power steering apparatus includes a valve rotary 102 having six valve grooves 100 and 101 extending along an axial direction on an outer circumferential surface thereof, as shown in FIGS. 14 and 15. Fitted on the outer circumference of the valve rotor 102, there is a valve sleeve 105 formed with the same number of valve grooves 103, 104 extending along the axial direction on the inner circumferential surface. Each of the valve grooves 100 and 101 of the valve rotor 102 has radial through holes (pump pots) 106 formed in the valve sleeve 105 and radial through holes formed in the valve rotor 102. It communicates with a pump and a tank alternately through the hole (tank loot) 107. On the other hand, the valve grooves 103 and 104 of the valve sleeve 105 are alternately communicating with both operating chambers of the power cylinder via the cylinder ports 108 and 109.

In a rotary valve of a conventional power steering device, for example, the valve groove 100 (101) (103) (104) moves relatively by turning the handle to the right (the valve rotary rotates in the direction of the arrow of FIG. 15). As shown in FIG. 16, the fluid flows from the pump pot 106 to the tank pot 107 until the flow path is completely switched. The pump pot 106 and the tank pot 107 are both Since the through-hole is a small diameter, the mainstream of the fluid flowing from the pump pot 106 to the tank pot 107 does not flow widely through the entire length of the chamfers 100a and 101a, but the chamfer 100a ( Since only the central portion of 101a) flows, there is a problem that the flow velocity is fast and abnormal sounds are likely to occur.

The present invention has been made to solve the above problems, the power flow that can prevent the generation of fluid sound by slowing the flow rate by passing the mainstream of the fluid flowing from the pump port to the tank port through the entire length of the chamfer To provide a rotary valve for the device.

The rotary valve of the power steering apparatus according to the present invention is a valve rotor having an even number of valve grooves extending in the axial direction on an outer circumferential surface thereof, fitted to the outer circumference of the valve rotor, and the same number of valve rotors as described above on the inner circumferential surface, There is a valve sleeve having a valve groove extending along the axial direction, and each valve groove is formed in two operating chambers of a pump, a tank, and a power cylinder through a passage hole formed at one of the valve rotor and the valve sleeve. The concave portion having a length along the axial direction is enlarged in the axial direction, or the area of the opening of the passage hole communicating the valve groove with the tank, or the valve groove communicating with the pump. It forms so that it may form or serve as both structures.

In the rotary valve of the power steering apparatus according to the present invention, the area of both or both of the passage hole from the pump and the passage hole to the tank is enlarged in the axial direction of the valve. The flow rate of the fluid flowing in the furnace enlarges, and the flow velocity decreases, and as a result, the fluid sound decreases.

EXAMPLE

Hereinafter, the present invention will be described by the embodiments shown in the drawings. 1 is a view showing the valve groove of the rotary valve of the power steering apparatus according to an embodiment of the present invention, and FIG. 2 is a cross-sectional view of the rotary valve. The valve rotor 2 has valve grooves 4 and 6 extending along the axial direction of an even number (6 in this embodiment) at regular intervals on the outer circumferential surface thereof. On both sidewalls of each of these valve grooves 4 and 6, chamfers 4a and 6a shorter than the lengths of the grooves 4 and 6 are formed. On the other hand, on the inner circumferential surface of the valve sleeve 8, valve grooves 10, 12 extending in the same number of axial directions as the valve rotor 2 are formed, and the valve sleeve 8 is a valve rotor 2 The valve grooves 4, 6, 10, 12 are connected via a torsion bar 14 at the same time so that the valve grooves 4, 6, 10, 12 are overlapped with the valve grooves positioned near both sides of the other side. have.

Radial through-holes (pump pots) 16 are formed in the lands between the valve grooves 10 and 12 of the valve sleeve 8 at intervals of one, and the three valves of the valve rotor 2 are formed. The hydraulic oil discharged from the pump is introduced into the groove 4. In addition, three through holes (tank pots) 18 are provided on the front surface of each valve groove 6 positioned between the three valve grooves 4 through these pumps in parallel along the axial direction (up and down in FIG. 1). These valve grooves 6 are formed in communication with the tank via the internal space 2a of the valve rotor 2. The distance between both ends of the three through holes 18 is slightly longer than the length of the chamfers 4a and 6a.

Radial through-holes (cylinder ports) 20 and 22 are formed in the bottom of each valve groove 10 and 12 of the valve sleeve 8, and six valve grooves 10 and 12 are formed. Are alternately connected to the two operating chambers of the power cylinder.

In the rotary valve according to the above configuration, the valve grooves 4 and 6 of the valve rotor 2 and the valve grooves 10 and 12 of the valve sleeve 8 are respectively inoperable (neutral state). Since it overlaps, the hydraulic oil introduced into the valve groove 4 of the valve rotor 2 from the pump pot 16 is the valve grooves 10 and 12 of the valve sleeve 8 located at both sides, and the valve rotor ( It is returned to the tank via the other valve groove 6 and tank pot 18 of 2).

When the valve rotor 2 rotates according to the operation of the handle, the valve grooves 4 and 6 of the valve rotor 2 and the valve grooves 10 and 12 of the valve sleeve 8 move relatively. As shown in FIG. 3, the valve groove 4 leading to the pump port 16 greatly overlaps the valve groove 10 leading to one cylinder port 20 formed in the valve sleeve 8. The valve groove 12 which communicates with the valve groove 12 which communicates with the other cylinder port 22 via only the chamfer 4a, and the valve groove 6 which communicates with the tank port 18 is connected to the valve groove 12. It greatly overlaps and communicates with the other valve groove 10 via only the chamfer 6a. The hydraulic oil flowing from the pump pot 16 to the tank pot 18 passes through the entire length in the axial direction of the chamfers 4a and 6a until the state is changed to this state. It becomes slow, which can reduce the occurrence of abnormal sounds. In addition, although the number of the through-holes 18 was three in the above-mentioned embodiment, it is not limited to this, It is good if two, four, etc. are multiple.

4 and 5 are views showing the second embodiment, wherein the tank pot 118 formed in the valve groove 6 of the valve rotor 2 has the chamfers 4a and 6a along the axial direction. It is a little longer than the hole. The other part is the same as the above embodiment, and the description is omitted. Also in this embodiment, it is possible to slow down the flow rate of the working oil flowing from the pump pot 16 to the tank pot 118, thereby preventing the occurrence of fluid sound.

5 and 6 are views showing the third embodiment, the tank port 218 is a through hole facing in the radial direction as in the prior art, and in the valve side opening of the port 218, A concave portion 219 having a width substantially the same as the diameter of the pot and having a depth of approximately the same length as the chamfers 4a and 6a is formed. Also in this embodiment, the hydraulic oil flowing from the pump port 16 flows through the entire length of the chamfers 4a and 6a into the shallow recess 219 and then flows out of the tank port 218. Therefore, the flow rate from the pump pot 16 to the tank pot 218 becomes slow, and generation of fluid sound can be suppressed.

8 and 9 show the fourth embodiment, in which the tank port 18 is a single through hole, while the valve side of the pump port 316 is a radial through hole. In the opening portion, a recessed depth 317 having the same depth as that of the tank pot 218 of the above-described fifth embodiment is formed. In this embodiment, the hydraulic oil flowing from the pump pot 316 spreads over the entire interior of the shallow depth recess 317 and then from the tank pot 18 through the entire length of the chamfers 4a and 6a. Spills.

10 and 11 show the embodiment of FIG. 5, in which the tank pot 418 is formed with a recess 419 having the same depth as the embodiment of FIG. 6 and having a pump cloth. The haute 416 is formed with a shallow depth of depression 417, which is the same as the embodiment of FIG. 8. In this case, since it flows into the recess 419 of the tank port 418 via the chamfers 4a and 6a from the recess 417 of the pump port 416, the flow range of the hydraulic oil is wider. As a result, a larger fluid sound reduction effect can be obtained.

In addition to each of the above-described embodiments, for example, a plurality of tank ports 18 of the embodiment of FIG. 1 and a pump port 316 having recesses 317 of the embodiment of FIG. 8 may be combined, The tank pot 118 of the embodiment of FIG. 1 and the pump pot 316 with the recess 317 of the embodiment of FIG. 8 may be combined. In addition, in the case where the recesses are formed in the openings of the plurality of tank ports 18 in FIG. 1 and are combined with the sole pump port 18 or the pump port 316 having the recesses 317, the fluid sound A reducing effect can be obtained.

In each of the above-described embodiments, the tank pots 18, 118, 218, and 418 are formed in the valve rotor 2, and as shown in FIGS. 12 and 13, the tank Even when the pot 518 is formed in the valve sleeve 8 together with the other pump pot 16 and both cylinder pots 20 and 22, the recess 519 is provided in the opening. By the method of the above, the same effect as the above-mentioned embodiment can be obtained.

As described above, by expanding the opening area of the pump pot or the tank pot into the valve along the axial direction, the speed of the fluid flowing from the pump to the tank can be slowed to reduce the occurrence of abnormal noise.

Claims (3)

A valve rotor 2 having an even number of valve grooves 4 and 6 extending in the axial direction on the outer circumferential surface thereof is fitted to the outer circumference of the valve rotor 2, and is flush with the valve rotor described above on the inner circumferential surface thereof. There is a valve sleeve (8) having a valve groove (10) and (12) is formed extending along the valve groove, each of the valve grooves in the operating chamber formed on either one of the valve rotor (2) and the valve sleeve (8) In the rotary valve of the power steering device in communication, The rotary valve of the power steering apparatus characterized in that the area of the opening of the passage hole communicating with the tank is enlarged in the axial direction. 2. The rotary valve of claim 1, wherein a concave portion 219 having a length in the axial direction is formed around the through hole communicating the valve groove with the pump. The concave portion according to claim 1, wherein the area of the opening of the passage hole for communicating the valve groove with the tank is enlarged in the axial direction, and the recess is elongated in the axial direction around the passage hole for communicating the valve groove with the pump. A rotary valve of the power steering apparatus, characterized in that 317 is formed.