A low-hydraulic rotary valve structure with an anti-jamming clutch

Abstract

This invention provides a low-hydraulic rotary valve structure with an anti-jamming clutch, comprising: a valve sleeve, an outer valve core, an inner valve core, a ball, a pressure plate, and a spring. The inner valve core is connected to a motor shaft and rotates with the motor shaft. The outer valve core is fitted onto the outside of the inner valve core from its bottom, and the valve sleeve is fitted onto the outside of the outer valve core from its bottom. Multiple V-shaped grooves are evenly distributed around the top end face of the outer valve core, and a ball is placed within each V-shaped groove. The pressure plate and spring are both fitted onto the motor shaft, and the spring presses the ball against the pressure plate, causing the bottom of the outer valve core to contact the bottom of the inner valve core within the valve sleeve. The oil passage on the outer valve core is the same as that on the valve sleeve, used to achieve oil passage communication between the valve sleeve and the inner valve core. When jamming occurs between the inner and outer valve cores, increasing the input torque of the motor shaft allows the outer valve core to overcome the spring force, thereby driving both the inner and outer valve cores to rotate simultaneously, ensuring normal valve function and achieving anti-jamming.

Description

Technical Field

[0001] This invention relates to the technical field of rotary direct-drive servo valves for aviation hydraulic actuation, and in particular to a low-hydraulic-power rotary valve structure with an anti-jamming clutch. Background Technology

[0002] With the rapid development of aviation hydraulic actuation technology, rotary direct-drive servo valves have been widely used. Compared with traditional electro-hydraulic servo valves, rotary direct-drive servo valves significantly reduce internal leakage, thereby reducing power consumption. The valve core, as the main component controlling the valve's output flow, is directly connected to and rotates coaxially with the motor shaft. Flow regulation is achieved through the geometry of the oil groove and the angular stroke.

[0003] However, to ensure the flow characteristics of direct-drive rotary servo valves, the valve core rotation stroke is usually limited to a certain range. Therefore, the geometry of the valve core throttling groove determines the structure of the fluid channel, which in turn limits the hydraulic force.

[0004] As aviation hydraulic components develop towards higher power and higher power-to-weight ratio, in order to improve the power of rotary direct drive servo valves and reduce power consumption, it is necessary to solve the problem of fluid force generated by large-flow rotary valve structures. Summary of the Invention

[0005] This invention provides a low-hydraulic-force rotary valve structure with an anti-jamming clutch, which solves the fluid force problem generated by high-flow rotary valve structures.

[0006] This invention provides a low-hydraulic rotary valve structure with an anti-jamming clutch, comprising: a valve sleeve 1, an outer valve core 2, an inner valve core 3, a ball 4, a pressure plate 5, and a spring 6, wherein:

[0007] The inner valve core 3 is connected to the motor shaft and rotates with the motor shaft; the outer valve core 2 is sleeved on the outside of the inner valve core 3 from the bottom, and the valve sleeve 1 is sleeved on the outside of the outer valve core 2 from the bottom.

[0008] The top end face of the outer valve core 2 is evenly distributed with multiple V-shaped grooves, and a ball 4 is provided in the V-shaped groove. The pressure plate 5 and the spring 6 are both sleeved on the motor shaft. The spring 6 presses the ball 4 through the pressure plate 5, so that the bottom of the outer valve core 2 contacts the bottom of the valve sleeve 1.

[0009] The oil passage on the outer valve core 2 is the same as that on the valve sleeve 1, which is used to realize the oil passage connection between the valve sleeve 1 and the inner valve core 3.

[0010] When the inner valve core 3 and the outer valve core 2 are stuck, increasing the input torque of the motor shaft can make the outer valve core 2 overcome the elastic force of the spring 6, thereby driving the inner valve core 3 and the outer valve core 2 to rotate simultaneously to ensure the normal function of the rotary valve and achieve anti-jamming.

[0011] Optionally, the valve sleeve 1 and the outer valve core 2 are placed coaxially within the valve body with clearance fit.

[0012] Optionally, the outer valve core 2 and the inner valve core 3 are coaxially placed inside the valve sleeve 1 with clearance fit.

[0013] Optionally, the inner valve core 3 is provided with three radially penetrating oil passages, which are distributed on three parallel planes; the axial directions of the three oil passages are not parallel to each other.

[0014] Optionally, the cross-section of the three oil passage holes is rectangular.

[0015] Optionally, the cross-section of the oil inlet and control hole on the valve sleeve 1 is rectangular; the cross-section of the oil return hole is circular.

[0016] Optionally, the cross-sectional dimensions of each oil passage hole on the outer valve core 2 are smaller than the cross-sectional dimensions of each oil passage hole on the valve sleeve 1.

[0017] Optionally, the angle between the first and second lines is greater than 21°;

[0018] The first connecting line is the line connecting the center of the throttling orifice of the inner valve core 3 and the center of the circle of the inner valve core 3.

[0019] The second connection is the outer edge of the control hole of the outer valve core 2;

[0020] The angle between the third and fourth lines is greater than 21°;

[0021] The third line is the line connecting the edge of the throttling orifice of the inner valve core 3 and the center of the inner valve core 3.

[0022] The fourth line is the radial edge of the inner valve core 3.

[0023] This invention provides a low-hydraulic-power rotary valve structure with an anti-jamming clutch. The low-hydraulic-power design of the rotary valve structure can reduce the input torque requirement of the servo valve and the system power consumption. The clutch ensures that flow control can still be achieved even if there is mechanical jamming inside the rotary valve, thereby ensuring the high reliability and high safety of the servo valve. Attached Figure Description

[0024] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the embodiments of the present invention will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0025] Figure 1 This is a schematic diagram of the structure of a low-hydraulic rotary valve with an anti-jamming clutch according to the present invention;

[0026] Figure 2for Figure 1 Cross-sectional view at point B in the middle;

[0027] Figure 3 for Figure 1 Cross-sectional view at point A in the middle;

[0028] Figure 4 for Figure 1 Cross-sectional view at point C;

[0029] Figure 5 This is a partially enlarged view of the oil in the rotary valve assembly according to an embodiment of the present invention, showing the oil flowing from the inlet through the throttling edge to the second control chamber.

[0030] Figure 6 This is a partially enlarged view of the oil flow from the first control chamber through the throttling edge to the return oil in a rotary valve assembly according to an embodiment of the present invention;

[0031] Figure 7 This is a cross-sectional view of the flow channel connecting the inner and outer valve cores of the rotary valve assembly to the second control chamber when the valve cores are stuck, according to an embodiment of the present invention.

[0032] Figure 8 This is a cross-sectional view of the flow channel connecting the inner and outer valve cores of the rotary valve assembly to the first control chamber when the valve cores are stuck, according to an embodiment of the present invention.

[0033] Among them: 1-valve sleeve, 2-outer valve core, 3-inner valve core, 4-ball, 5-pressure plate, 6-spring. Detailed Implementation

[0034] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0035] The features and illustrative embodiments of various aspects of the present invention will now be described in detail. Numerous specific details are set forth in the following detailed description to provide a thorough understanding of the invention. However, it will be apparent to those skilled in the art that the invention may be practiced without requiring some of these specific details. The following description of embodiments is merely intended to provide a better understanding of the invention by illustrating examples of the invention. The invention is by no means limited to any specific setups and methods set forth below, but covers any improvements, substitutions, and modifications to structures, methods, and devices without departing from the spirit of the invention. Well-known structures and techniques are not shown in the drawings and the following description to avoid unnecessarily obscuring the invention.

[0036] It should be noted that, unless otherwise specified, the embodiments of the present invention and the features thereof can be combined with each other, and the various embodiments can be referenced and cited in each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0037] like Figure 1-8 This invention provides a low-hydraulic rotary valve structure with an anti-jamming clutch, the structure comprising: a valve sleeve 1, an outer valve core 2, an inner valve core 3, a ball 4, a pressure plate 5, and a spring 6, wherein:

[0038] The valve sleeve 1 includes fourteen oil passage holes on three planes, including oil inlet holes, oil return holes, and control holes, which are placed in the valve body and are in a constrained state;

[0039] The outer valve core 2 includes fourteen oil passage holes on three planes, including an oil inlet hole, an oil return hole, and a control hole;

[0040] The valve sleeve 1 and the outer valve core 2 are placed coaxially in the valve body and are fitted with a clearance. The outer valve core 2 can rotate relative to the valve sleeve 1, and one side is constrained to translate along the axis.

[0041] The inner valve core 3 includes three radially penetrating and intersecting oil passage holes on three planes. By controlling the rotation angle of the inner valve core, the oil passages of the outer valve core and the valve sleeve are connected respectively to form a flow channel.

[0042] The outer valve core 2 and the inner valve core 3 are coaxially placed inside the valve sleeve 1 and are fitted with a clearance, allowing them to rotate relative to each other;

[0043] The valve sleeve 1, outer valve core 2, and inner valve core 3 together form a flow channel through the oil passage holes in their structure, thereby realizing the function of rotary valve flow control.

[0044] The oil passage orifice includes its geometric shape, which is determined by the cross-sectional shape of the oil passage orifice. Changing the structure of the oil passage orifice can adjust the hydraulic force of the rotary valve. When a specific jet angle is met, the hydraulic force can be basically eliminated, thereby reducing the power consumption required to drive the rotary valve.

[0045] The ball 4 fits into the groove on the end face of the outer valve core 2, and the other side is in direct contact with the pressure plate 5;

[0046] One side of the spring 6 is fixed and constrained, and is in a compressed state. The other side transmits the elastic force to the ball 4 through the pressure plate 5, thereby pressing the outer valve core 2.

[0047] Under normal operating conditions, the outer valve core 2 and valve sleeve 1 remain stationary. The inner valve core 3 is rotated by input torque to achieve flow control. When the inner valve core 3 and the outer valve core 2 are stuck, increasing the input torque can make the outer valve core 2 overcome the elastic force of the spring 6, thereby controlling the inner valve core 3 and the outer valve core 2 to rotate simultaneously to ensure the normal function of the rotary valve and achieve the anti-jamming design.

[0048] Figure 1 This is a cross-sectional schematic diagram of a low-hydraulic rotary valve with an anti-jamming clutch according to the present invention.

[0049] like Figure 1 As shown, the present invention provides a low-hydraulic rotary valve structure with an anti-jamming clutch, comprising: valve sleeve 1, outer valve core 2, inner valve core 3, ball 4, pressure plate 5, and spring 6.

[0050] Figure 2 , Figure 3 , Figure 4 When the inner valve core 3 rotates at a certain angle Figure 1 The flow channel cross-sectional view at positions B, A, and C in the diagram shows that the oil inlet is connected to the second control chamber, and the oil return is connected to the first control chamber. The rotation angle of the inner valve core 3 is controlled by an external input torque to meet the flow control function of the rotary valve structure.

[0051] Figure 2 This is a cross-sectional view of the flow channel of the oil inlet of the rotary valve assembly connected to the second control chamber according to an embodiment of the present invention.

[0052] The valve sleeve 1 may include a first oil inlet hole 1a, a second oil inlet hole 1b, a first oil return hole 1c, a second oil return hole 1d, a first control hole 1e, a second control hole 1f, a third control hole 1g, and a fourth control hole 1h.

[0053] The outer valve core 2 may include an outer valve core first oil inlet hole 2a, an outer valve core second oil inlet hole 2b, an outer valve core first control hole 2c, an outer valve core second control hole 2d, an outer valve core third control hole 2e, and an outer valve core fourth control hole 2f;

[0054] The inner valve core 3 may include an oil inlet throttling hole 3a. In the position shown in the figure, the inner valve core 3 rotates counterclockwise and forms two oil inlet paths with the valve sleeve 1 and the outer valve core 2, namely 1a-2a-3a-2c-1e and 1b-2b-3a-2f-1h. High-pressure oil enters the second control chamber through the oil inlet path.

[0055] Figure 3 This is a cross-sectional view of the flow channel of the rotary valve assembly connected to the first control chamber according to an embodiment of the present invention;

[0056] The valve sleeve 1 may include a first return oil hole 1c, a second return oil hole 1d, a fifth control hole 1i, and a sixth control hole 1j; the outer valve core 2 may include a fifth control hole 2g, a sixth control hole 2h, a first return oil hole 2i, and a second return oil hole 2j; the inner valve core 3 may include a first return oil throttling hole 3b. In the position shown in the figure, the inner valve core 1 rotates counterclockwise, forming two return oil paths with the valve sleeve 1 and the outer valve core 2, namely 1i-2g-3b-2i-1d and 1j-2h-3b-2j-1c, respectively. The oil enters the return oil path from the first control chamber.

[0057] Figure 4 This is a cross-sectional view of the rotary valve assembly in an embodiment of the present invention, showing that the return oil is not connected to the flow channel of the second control chamber.

[0058] The valve sleeve 1 may include a first return oil hole 1c, a second return oil hole 1d, a seventh control hole 1k, and an eighth control hole 1l; the outer valve core 2 may include a seventh control hole 2k, an eighth control hole 2l, a third return oil hole 2m, and a fourth return oil hole 2n; the inner valve core 3 may include a second return oil throttling hole 3c. In the position shown in the figure, the inner valve core 1 rotates counterclockwise and does not form a return oil path with the valve sleeve 1 and the outer valve core 2, indicating that the return oil is not connected to the second control cavity.

[0059] Figure 5 This is a partially enlarged view of the oil in the rotary valve assembly according to an embodiment of the present invention, showing the oil flowing from the inlet through the throttling edge to the second control chamber;

[0060] Among them, the structure of the first control hole 2c of the outer valve core can be designed to meet α≥21° and β≥21°, thereby basically eliminating the hydraulic force in the oil inlet circuit of the rotary valve structure.

[0061] Figure 6 This is a partially enlarged view of the oil flow from the first control chamber through the throttling edge to the return oil in a rotary valve assembly according to an embodiment of the present invention;

[0062] Among them, the fifth control hole 2g structure of the outer valve core can be designed to meet α≥21° and β≥21°, thereby basically eliminating the hydraulic force in the return oil circuit of the rotary valve structure.

[0063] Figure 7 , Figure 8 The figures show cross-sectional views of the flow channels of the rotary valve at different sections when the outer valve core 2 and the inner valve core 3 rotate together at a certain angle under jamming conditions. The positions shown correspond to the oil inlet and the second control chamber being connected, and the oil return and the first control chamber being connected. The rotation angle is controlled by an external input torque to ensure that the rotary valve structure can still achieve the function of flow control under jamming conditions.

[0064] Figure 7This is a cross-sectional view of the flow channel connecting the inner and outer valve cores of the rotary valve assembly to the second control chamber when the valve cores are stuck, according to an embodiment of the present invention.

[0065] Among them, the outer valve core 2 and the inner valve core 1 are stuck and remain in a fixed relative position. As the input torque increases, the outer valve core 2 and the inner valve core 1 are driven to rotate simultaneously against the spring force, forming two oil inlet paths with the valve sleeve 1, namely 1a-2a-1e and 1b-2b-1h. The high-pressure oil enters the second control chamber through the oil inlet path.

[0066] Figure 8 This is a cross-sectional view of the flow channel connecting the inner and outer valve cores of the rotary valve assembly to the first control chamber when the valve cores are stuck, according to an embodiment of the present invention.

[0067] Among them, the outer valve core 2 and the inner valve core 1 are stuck and remain in a fixed relative position. As the input torque increases, the outer valve core 2 and the inner valve core 1 are driven to rotate simultaneously against the spring force, forming two return oil paths with the valve sleeve 1, namely 1i-2i-1d and 1j-2j-1c. The oil enters the return oil path from the first control chamber.

[0068] In some embodiments, the cross-sectional shape and size of the oil passage holes of the valve sleeve 1, the outer valve core 2, and the throttling hole of the inner valve core 3 can be adjusted together. The shape can be adjusted to be rectangular or circular, thereby obtaining different maximum control flow rates and hydraulic forces.

[0069] In some embodiments, the maximum control flow rate and hydraulic force can be adjusted simply by adjusting the size of the throttling orifice of the inner valve core 3, resulting in different valve flow gains.

[0070] In some embodiments, adjusting the spring size and clamping state can change the clutch starting torque.

[0071] Extensive experiments have demonstrated that a low-hydraulic-force rotary valve structure with an anti-jamming clutch can not only achieve high-flow control and essentially eliminate hydraulic forces, but also ensure the normal operation of the rotary valve even when the inner and outer valve cores are jammed.

[0072] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, but the protection scope of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in the present invention, and these modifications or substitutions should be covered within the protection scope of the present invention.

Claims

1. A low-hydraulic rotary valve structure with an anti-jamming clutch, characterized in that, include: Valve sleeve (1), outer valve core (2), inner valve core (3), ball (4), pressure plate (5), spring (6), wherein: The inner valve core (3) is connected to the motor shaft and rotates with the motor shaft; the outer valve core (2) is sleeved on the outside of the inner valve core (3) from the bottom, and the valve sleeve (1) is sleeved on the outside of the outer valve core (2) from the bottom; The top end face of the outer valve core (2) is evenly distributed with multiple V-shaped grooves, and a ball (4) is provided in the V-shaped groove. The pressure plate (5) and the spring (6) are both sleeved on the motor shaft. The spring (6) presses the ball (4) through the pressure plate (5) so that the bottom of the outer valve core (2) contacts the bottom of the valve sleeve (1). The oil circuit on the outer valve core (2) is the same as that on the valve sleeve (1), which is used to realize the oil circuit connection between the valve sleeve (1) and the inner valve core (3); When the inner valve core (3) and the outer valve core (2) are stuck, increasing the input torque of the motor shaft can make the outer valve core (2) overcome the elastic force of the spring (6), thereby driving the inner valve core (3) and the outer valve core (2) to rotate at the same time to ensure the normal function of the rotary valve and achieve anti-sticking.

2. The low-hydraulic rotary valve structure with anti-jamming clutch according to claim 1, characterized in that, The valve sleeve (1) and the outer valve core (2) are placed coaxially in the valve body with clearance fit.

3. The low-hydraulic rotary valve structure with anti-jamming clutch according to claim 1, characterized in that, The outer valve core (2) and the inner valve core (3) are placed coaxially inside the valve sleeve (1) with clearance fit.

4. The low-hydraulic rotary valve structure with anti-jamming clutch according to claim 1, characterized in that, The inner valve core (3) is provided with three radially penetrating oil passages, which are distributed on three parallel planes; the axial directions of the three oil passages are not parallel to each other.

5. The low-hydraulic rotary valve structure with anti-jamming clutch according to claim 4, characterized in that, The cross-sections of the three oil passage holes are rectangular.

6. The low-hydraulic rotary valve structure with anti-jamming clutch according to claim 4, characterized in that, The inlet and control holes on the valve sleeve (1) have rectangular cross-sections; the return hole has a circular cross-section.

7. The low-hydraulic rotary valve structure with anti-jamming clutch according to claim 6, characterized in that, The cross-sectional dimensions of each oil passage hole on the outer valve core (2) are smaller than the cross-sectional dimensions of each oil passage hole on the valve sleeve (1).

8. The low-hydraulic rotary valve structure with anti-jamming clutch according to claim 7, characterized in that, The angle between the first and second lines is greater than 21°; The first connecting line is the line connecting the center of the throttling orifice of the inner valve core (3) and the center of the circle of the inner valve core (3); The second connection line is the outer edge of the control hole of the outer valve core (2); The angle between the third and fourth lines is greater than 21°; The third line is the line connecting the edge of the throttling orifice of the inner valve core (3) and the center of the inner valve core (3); The fourth line is the radial edge of the inner valve core (3).

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