Throttling device and static pressure device

Abstract

The application discloses a throttler and static pressure equipment, the throttler comprises a base, a diaphragm, a rotating body and a cover plate. The base has a first side and a second side, the first side is provided with a first groove, the first groove is provided with a first channel, the second side is provided with a recess, the recess is used for surrounding the predetermined equipment to form an oil supply channel, the base is further provided with an oil supply port, a first throttling channel and a second throttling channel. The diaphragm is arranged in the first groove, and the diaphragm and the first groove surround to form a pressure stabilizing cavity. The rotating body is provided with an overflow channel, the rotating body is rotatably arranged in the first groove, the rotating body and the diaphragm surround to form a pressure regulating cavity, the rotating body and the base are provided with a second channel, the second channel is provided with a first opening, the first opening is in communication with the first end of the second throttling channel and the first opening. The application solves the problem of poor adaptability of the existing throttler.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of mechanical processing, and in particular, to a flow restrictor and a hydrostatic equipment. BACKGROUND

[0002] In some existing hydrostatic equipment, such as a hydrostatic guide rail, a hydrostatic spindle or a hydrostatic rotary table, a hydrostatic cavity is arranged between components to reduce friction when the components move relative to each other, thereby improving the running accuracy and processing accuracy of the hydrostatic equipment. In addition, the hydrostatic equipment usually needs to be equipped with a flow restricting device. The flow restrictor adjusts the flow of oil entering the hydrostatic cavity, thereby changing the load capacity of the hydrostatic equipment.

[0003] However, when the working condition of the hydrostatic equipment changes, the existing flow restrictor is difficult to adapt to the working condition of the hydrostatic equipment, that is, the existing flow restrictor has poor adaptability. SUMMARY

[0004] The main purpose of the present application is to provide a flow restrictor and a hydrostatic equipment to at least solve the problem of poor adaptability of the flow restrictor in the prior art.

[0005] According to one aspect of the present application, a flow restrictor is provided, comprising:

[0006] a base having a first side and a second side arranged opposite to each other, the first side of the base being provided with a first recess, the first recess being provided with a first channel therein, the first channel extending from the first side to the second side, the second side of the base being provided with a recessed portion, the recessed portion being used to form an oil supply channel with a predetermined equipment, the base being further provided with an oil supply port, a first flow restricting channel and a second flow restricting channel, the oil supply port being in communication with the oil supply channel and the second flow restricting channel, a first end of the second flow restricting channel extending to the first side, a second end of the second flow restricting channel extending to the second side;

[0007] a diaphragm arranged in the first recess, the diaphragm and the first recess forming a pressure stabilizing cavity;

[0008] A rotating body is provided with an overflow channel, and is arranged at least partially rotatably in the first groove and on the side of the film away from the groove bottom of the first groove. A pressure regulating cavity is formed between the rotating body and the film. A second channel is arranged between the rotating body and the base, and a first opening is arranged on the second channel. The first opening is in communication with the first end of the second throttle channel and the first opening. The first end of the overflow channel is in communication with the second channel, and the second end of the overflow channel is in communication with the pressure regulating cavity. The rotating body rotates to increase or decrease the distance between the first opening and the first end of the overflow channel.

[0009] A cover plate is arranged on the first side and the rotating body.

[0010] The two ends of the first throttle channel are in communication with the oil supply channel and the pressure stabilizing cavity, respectively. The second end of the second throttle channel is in communication with the oil supply channel. The first channel is in communication with the static pressure cavity of the predetermined device and the oil supply channel.

[0011] Further, the first side is also provided with a second groove, and the second groove is located on the outer periphery of the first groove. The first opening is arranged in the second groove.

[0012] The rotating body overlaps the second groove and forms the second channel with the second groove.

[0013] Further, the rotating body has an outer flange which protrudes from the rotating body in a direction away from the center of rotation of the rotating body and is located on the outer side of the first groove. The outer flange overlaps the second groove, and the overflow channel is arranged between the rotating body and the outer flange.

[0014] Further, a first overflow groove is arranged on the side of the outer flange close to the second groove, and the first overflow groove is in communication with the second groove. A second overflow groove is arranged on the outer periphery of the rotating body in the first groove and is in communication with the first overflow groove. The first overflow groove and the second overflow groove form the overflow channel.

[0015] Further, the first groove includes a circular groove, and the second groove includes a circular ring groove. The circular ring groove is coaxially arranged with the circular groove.

[0016] The rotating body includes a circular rotating body which rotates around the axis of the circular groove under the action of an external force.

[0017] Further, the cover plate is provided with an avoiding through hole extending along the height direction of the flow restrictor, the rotating body is provided with a boss on the side away from the base, the boss is at least partially located in the avoiding through hole, and the boss is provided with a rotating part on the side away from the base.

[0018] Further, the overflow channel is arranged on the side wall surface of the rotating body, the rotating body is provided with an identification part on the side away from the first groove, and in the projection of the height direction of the flow restrictor, the projection of the identification part and the projection of the overflow channel are located on the same straight line from the geometric center of the projection surface of the rotating body to the outside of the rotating body.

[0019] Further, the base is provided with a third flow-restricting channel, the first end of the third flow-restricting channel extends to the pressure regulating cavity, the second end of the third flow-restricting channel extends to the second side surface, and the minimum cross-sectional area of the third flow-restricting channel is smaller than the minimum cross-sectional area of the overflow channel.

[0020] Further, the first groove is provided with a flow-restricting boss, the first channel is arranged on the flow-restricting boss, the diaphragm and the space in the first groove outside the flow-restricting boss form the pressure stabilizing cavity; and / or,

[0021] The rotating body is provided with a spiral groove on the side close to the diaphragm, the center of the spiral groove is located on the axis of the rotating body, and the spiral groove is in communication with the pressure regulating cavity.

[0022] In another aspect, the application further provides a static pressure device, which comprises the flow restrictor.

[0023] Compared with the flow restrictor of the prior art, the flow restrictor of the application can not only automatically adjust the flow of the oil entering the static pressure cavity through the pressure feedback mode of the static pressure cavity, but also can adjust the pressure of the oil in the pressure regulating cavity by actively rotating the rotating body, thereby further adjusting the flow of the oil entering the static pressure cavity of the flow restrictor, that is, the flow adjustment range of the flow restrictor of the application is wider, and the adaptability is higher. BRIEF DESCRIPTION OF DRAWINGS

[0024] The accompanying drawings, which are included to provide a further understanding of the application, form a part of the application and illustrate the illustrative embodiments of the application and together with the description serve to explain the application. In the drawings:

[0025] Figure 1 FIG. 1 is a structural schematic diagram of the flow restrictor disclosed in the application;

[0026] Figure 2An exploded view of the flow restrictor disclosed in the present application;

[0027] Figure 3 A structural view of the base disclosed in the present application in a first perspective;

[0028] Figure 4 A structural view of the base disclosed in the present application in a second perspective;

[0029] Figure 5 A perspective view of the base disclosed in the present application in a third perspective (the overflow channel is not directly opposite the first opening);

[0030] Figure 6 A perspective view of the base disclosed in the present application in a fourth perspective (the overflow channel is not directly opposite the first opening);

[0031] Figure 7 A sectional view of the base disclosed in the present application;

[0032] Figure 8 A structural view of the rotating body disclosed in the present application in a fifth perspective;

[0033] Figure 9 A structural view of the rotating body disclosed in the present application in a sixth perspective;

[0034] Figure 10 A graph showing the relationship between the pressure on the static pressure cavity and the flow rate of the flow restrictor when the central angle A formed between the first end of the overflow channel and the straight line from the rotating center of the rotating body to the rotating center of the rotating body and the straight line from the first opening to the rotating center of the rotating body is different.

[0035] In the above drawings, the following reference signs are used:

[0036] 11, cover plate; 12, base; 13, rotating body; 14, diaphragm; 111, avoiding through hole; 121, first side surface; 122, second side surface; 123, second channel; 130, overflow channel; 131, outer flange; 132, boss; 1211, first groove; 1212, second groove; 1213, first throttling channel; 1214, second throttling channel; 1215, first channel; 1216, third throttling channel; 1221, recessed portion; 1222, oil supply port; 1301, first overflow groove; 1302, second overflow groove; 1311, helical groove; 1321, rotating portion; 1322, identification portion; 12111, throttling boss; 12112, bearing boss; 12121, first opening. DETAILED DESCRIPTION

[0037] It should be noted that the embodiments and the features in the embodiments in the present application can be combined with each other without conflict. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0038] It should be noted that the terms used herein are only intended to describe specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form, unless the context clearly indicates otherwise, and it should also be understood that the terms "comprise" and / or "include" as used herein indicate the presence of the features, steps, operations, devices, components and / or combinations thereof.

[0039] The relative arrangement of the components and steps, numerical expressions and values set forth in these embodiments do not limit the scope of the present application, unless otherwise specifically stated. At the same time, it should be understood that the sizes of the various parts shown in the drawings are not drawn in proportion to the actual proportions. Techniques, methods and devices known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered as part of the authorized description, if appropriate. In all examples shown and discussed herein, any specific value should be interpreted as merely exemplary, and not as a limitation. Therefore, other examples of exemplary embodiments can have different values. It should be noted that similar reference numbers and letters represent similar items in the following drawings, and therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0040] It can be known that most of the existing throttles for adjusting the static pressure cavity have fixed flow after the design parameters are fixed and cannot be changed. This will cause, for example, when the load force on the static pressure cavity is too large, the flow provided by the throttle cannot make the stiffness of the oil film in the static pressure cavity sufficient to support the load, eventually leading to the failure of the oil film in the static pressure cavity. That is to say, the existing throttle does not have adjusting ability, and the adaptability of the existing throttle is poor.

[0041] Referring to Figures 1 to 10 As shown, according to the embodiments of the present application, a static pressure device is provided, which can be a static pressure guide rail, a static pressure rotary table, or a static pressure spindle. The static pressure device includes a throttle, which includes a base 12, a diaphragm 14, a rotating body 13 and a cover plate 11.

[0042] The base 12 has a first side 121 and a second side 122 opposite to each other. The first side 121 of the base 12 is provided with a first recess 1211. The first recess 1211 is provided with a first channel 1215 extending from the first side 121 to the second side 122. The second side 122 of the base 12 is provided with a recessed portion 1221 for forming an oil supply channel with a predetermined device. The base 12 is further provided with an oil supply port 1222, a first throttling channel 1213 and a second throttling channel 1214. The oil supply port 1222 is in communication with the oil supply channel and the second throttling channel 1214. The first end of the second throttling channel 1214 extends to the first side 121, and the second end of the second throttling channel 1214 extends to the second side 122. The diaphragm 14 is arranged in the first recess 1211, and the diaphragm 14 and the first recess 1211 form a pressure stabilizing chamber. The rotating body 13 is provided with an overflow channel 130. The rotating body 13 is at least partially rotatably arranged in the first recess 1211 and located on the side of the diaphragm 14 away from the bottom of the first recess 1211. The rotating body 13 and the diaphragm 14 form a pressure regulating chamber therebetween. The rotating body 13 and the base 12 are provided with a second channel 123. The second channel 123 is provided with a first opening 12121. The first opening 12121 is in communication with the first end of the second throttling channel 1214 and the first opening 12121. The first end of the overflow channel 130 is in communication with the second channel 123, and the second end of the overflow channel 130 is in communication with the pressure regulating chamber. The rotating body 13 rotates to increase or decrease the distance between the first opening 12121 and the first end of the overflow channel 130. The cover plate 11 covers the first side 121 and the rotating body 13. The two ends of the first throttling channel 1213 are in communication with the oil supply channel and the pressure stabilizing chamber, respectively. The second end of the second throttling channel 1214 is in communication with the oil supply channel. The first channel 1215 is in communication with the static pressure chamber of the predetermined device and the oil supply channel.

[0043] Specifically, when the flow restrictor is installed on the static pressure device, the second side surface 122 is in sealing contact with the static pressure device, the oil inlet channel on the static pressure device is connected with the oil supply port 1222, the oil enters the flow restrictor through the oil supply port 1222, part of the oil enters the second channel 123 through the second throttling channel 1214 and the first opening 12121, and then the oil in the second channel 123 enters the pressure regulating cavity through the overflow channel 130. Part of the oil entering the oil supply port 1222 is located in the oil supply channel and flows to the first throttling channel 1213, and then flows into the pressure stabilizing cavity through the first throttling channel 1213, and part of the oil in the oil supply channel flows into the static pressure cavity of the static pressure device through the first channel 1215, thereby supplying oil to the static pressure cavity. When there is no load on the static pressure cavity of the static pressure device, the pressures of the oil in the pressure stabilizing cavity and the pressure regulating cavity are the same, at this time the diaphragm 14 is closed in the first channel 1215, and the oil in the pressure stabilizing cavity cannot enter the static pressure cavity through the first channel 1215. When there is a load in the static pressure cavity of the static pressure device, the load exerts pressure on the oil in the static pressure cavity, thereby transferring the pressure to the oil in the first channel 1215, the oil in the first channel 1215 exerts pressure on the diaphragm 14, thereby deforming the diaphragm 14 in the direction close to the rotating body 13, at this time the diaphragm 14 opens the first channel 1215, and the oil in the pressure stabilizing cavity can flow into the static pressure cavity through the first channel 1215, thereby increasing the thickness and rigidity of the oil in the static pressure cavity and improving the load capacity of the static pressure cavity.

[0044] In addition, since the rotating body 13 is provided with the overflow channel 130 and the rotating body 13 is partially rotatably arranged in the first groove 1211, when the rotating body 13 rotates, the distance between the first end of the overflow channel 130 and the first opening 12121 increases or decreases. When the distance between the first end of the overflow channel 130 and the first opening 12121 increases, it means that the oil entering the second channel 123 through the first opening 12121 needs to go through a longer path to enter the overflow channel 130, that is, the longer path causes the oil to bear greater resistance, and ultimately the pressure of the oil entering the pressure regulating cavity is smaller, and the pressure of the oil in the pressure stabilizing cavity is greater. The diaphragm 14 is more likely to be depressed and deformed in the direction close to the pressure regulating cavity under the pressure of the oil in the pressure stabilizing cavity, thereby making the oil in the pressure stabilizing cavity more likely to enter the static pressure cavity through the first channel 1215. In addition, when the distance between the overflow channel 130 and the first opening 12121 decreases, the pressure of the oil in the pressure regulating cavity increases, and the diaphragm 14 is not easily depressed and deformed in the direction close to the pressure regulating cavity, at this time the flow of the oil input to the static pressure cavity by the flow restrictor is reduced, and when the load on the static pressure cavity does not exceed the load capacity of the static pressure cavity, by reducing the distance between the first opening 12121 and the overflow channel 130, the oil consumption of the static pressure cavity can be reduced to a certain extent.

[0045] Compared with the thin film restrictor in the related art, the restrictor of the present application can not only automatically adjust the flow of the oil liquid entering the static pressure cavity through the pressure feedback mode of the static pressure cavity. At the same time, the restrictor of the present application can also adjust the pressure of the oil liquid in the pressure regulating cavity by actively rotating the rotating body 13, and further adjust the flow of the oil liquid flowing into the static pressure cavity of the restrictor, that is, the flow adjustment range of the restrictor of the present application is wider, and the adaptability is higher.

[0046] Further, the first side surface 121 is also provided with a second groove 1212, the second groove 1212 is located outside the first groove 1211, and the first opening 12121 is arranged in the second groove 1212. The rotating body 13 is lapped on the second groove 1212, and the second groove 1212 is formed with the second channel 123.

[0047] The second groove 1212 is not arranged in the restrictor of the related art, but is directly communicated with the pressure regulating cavity through the second restrictor channel 1214, which means that the pressure of the oil liquid in the pressure regulating cavity cannot be adjusted. In the embodiment, the independent second groove 1212 is designed, and the second groove 1212 is not directly communicated with the first groove 1211. When the rotating body 13 is lapped on the second groove 1212, the rotating body 13 and the second groove 1212 form the second channel 123, and the overflow channel 130 on the rotating body 13 is communicated between the second groove 1212 and the pressure regulating cavity. When the rotating body 13 is rotated, the distance between the first opening 12121 and the first end of the overflow channel 130 changes, thereby changing the pressure of the liquid entering the pressure regulating cavity.

[0048] Further, the rotating body 13 has an outer flange 131, the outer flange 131 protrudes from the rotating body 13 in a direction away from the center of rotation of the rotating body 13, and is located outside the first groove 1211. The outer flange 131 is lapped on the second groove 1212, and the overflow channel 130 is arranged between the rotating body 13 and the outer flange 131.

[0049] Specifically, the outer flange 131 is lapped on the second groove 1212, which forms the second channel 123 between the outer flange 131 and the second groove 1212 on one hand, and on the other hand, the outer flange 131 has a certain supporting effect on the rotating body 13, avoiding the rotating body 13 located in the first groove 1211 directly abutting against the diaphragm 14 under the action of gravity, causing the problem that there is no pressure regulating cavity between the diaphragm 14 and the rotating body 13. In addition, the overflow channel 130 is arranged between the rotating body 13 and the outer flange 131, so that the oil liquid in the second channel 123 can enter the pressure regulating cavity.

[0050] In some embodiments, a first overflow groove 1301 is provided on the side of the outer flange 131 near the second groove 1212, the first overflow groove 1301 communicates with the second groove 1212, and a second overflow groove 1302 communicating with the first overflow groove 1301 is provided on the outer peripheral surface of the rotating body 13 in the first groove 1211, the first overflow groove 1301 and the second overflow groove 1302 form an overflow channel 130.

[0051] Specifically, when the outer flange 131 overlaps with the second groove 1212, in the height direction of the throttle (as shown in the attached figure) Figure 2 In the projection (in the Z direction), the projection surface of the first overflow groove 1301 at least partially coincides with the projection surface of the second groove 1212, and regardless of the rotation angle of the rotating body 13, the projection surface of the first overflow groove 1301 still at least partially coincides with the projection surface of the second groove 1212, so that the oil in the second groove 1212 can always enter the first overflow groove 1301. Furthermore, the second overflow groove 1302 is disposed on the outer peripheral surface of the rotating body 13 located within the first groove 1211, and the oil in the first overflow groove 1301 can enter the pressure regulating chamber through the second overflow groove 1302. This embodiment has a simple structure, is easy to manufacture, and can reduce the manufacturing cost of the throttle to a certain extent.

[0052] Furthermore, the first groove 1211 includes a circular groove, and the second groove 1212 includes an annular groove, with the annular groove and the circular groove being coaxially arranged. The rotating body 13 includes a circular rotating body, which rotates around the axis of the circular groove under the action of an external force.

[0053] In other words, since the position of the first overflow groove 1301 remains unchanged, and the second groove 1212 is an annular groove and the first groove 1211 is a circular groove, both of which are coaxially arranged with the rotating body 13, when the rotating body 13 rotates around the axis of the circular groove, the oil in the second groove 1212 can always enter the first overflow groove 1301. In addition, the annular groove, the circular groove, and the circular rotating body are coaxially arranged to avoid eccentric movement between the circular rotating body and the circular groove or the annular groove when the circular rotating body rotates.

[0054] As attached Figure 2 and attached Figure 8 As shown, the cover plate 11 has a clearance through hole 111, which extends along the height direction of the throttle. The rotating body 13 has a boss 132 on the side away from the base 12. The boss 132 is at least partially located in the clearance through hole 111. A rotating part 1321 is provided on the side of the boss 132 away from the base 12.

[0055] Specifically, the boss 132 is at least partially located within the clearance through hole 111, so that the cover plate 11 has a certain limiting effect on the boss 132, improving the connection stability of the rotating body 13. In addition, a rotating part 1321 is provided on the side of the boss 132 facing away from the base 12, so that the operator can rotate the rotating part 1321 through the clearance through hole 111 to adjust the output flow rate of the throttle. In a specific embodiment, the side of the boss 132 facing away from the base 12 is flush with the side of the cover plate 11 facing away from the base 12, and the rotating part 1321 includes a rotating hole, which is formed at the geometric center of the side of the boss 132 facing away from the base 12.

[0056] In some embodiments, the cover plate 11 and the base 12 are connected by bolts. When the cover plate 11 is fixedly connected to the base 12 by bolts, the rotating body 13 is fixed, that is, the rotating body 13 cannot rotate at this time, so as to improve the stability of the throttle and prevent the rotating body 13 from being automatically rotated by external force when the throttle is working. When the operator wants to rotate the rotating body 13, he only needs to loosen the bolts and then rotate the rotating hole, which is convenient for adjustment.

[0057] In some embodiments, the throttle also includes a sealing ring disposed between the outer flange 131 and the base 12 to prevent oil leakage and to prevent the throttle from contaminating other components of the hydrostatic equipment. The sealing ring may also be disposed between the second side 122 and the hydrostatic equipment.

[0058] As attached Figure 9 As shown, the overflow channel 130 is provided on the side wall of the rotating body 13. A marking part 1322 is provided on the side of the rotating body 13 away from the first groove 1211. In the projection of the height direction of the throttle, the projection of the marking part 1322 and the projection of the overflow channel 130 are located on the same straight line from the geometric center of the projection surface of the rotating body 13 to the outside of the rotating body 13.

[0059] Specifically, since the rotating body 13 is a circular rotating body 13, and the overflow passage 130 is arranged on the side wall surface of the rotating body 13, when the projection of the identification part 1322 and the projection of the overflow passage 130 are located on the same straight line from the geometric center of the projection surface of the rotating body 13 to the outside of the rotating body 13 in the projection of the height direction of the throttle, the operator can know the position of the overflow passage 130 through the identification part 1322, so as to determine the distance between the first end of the overflow passage 130 and the first opening 12121. In some embodiments, the identification part 1322 is also arranged on the outer side wall surface of the base 12, so as to identify the position of the first opening 12121. In some specific embodiments, the identification part 1322 includes a marking hole arranged on the side of the boss 132 away from the base 12, and the operator can observe the marking hole through the avoiding through hole 111. The identification part 1322 also includes an identification line arranged on the outer side wall surface of the base 12, so as to identify the position of the first opening 12121. The user can determine the angle of rotation of the rotating body 13 through the marking hole and the identification line.

[0060] Further, the third throttle passage 1216 is arranged in the base 12, the first end of the third throttle passage 1216 extends to the pressure regulating cavity, the second end of the third throttle passage 1216 extends to the second side surface 122, and the minimum cross-sectional area of the third throttle passage 1216 is smaller than the minimum cross-sectional area of the overflow passage 130. It is worth mentioning that the minimum cross-sectional area of the third throttle passage 1216 is the cross-sectional area obtained by taking the position with the smallest radius of the third throttle passage 1216 in the plane perpendicular to the third throttle passage 1216, and similarly, the minimum cross-sectional area of the overflow passage 130 is the cross-sectional area obtained by taking the position with the smallest radius of the overflow passage 130 in the plane perpendicular to the overflow passage 130.

[0061] Unlike the related art, the oil in the pressure regulating cavity does not need to be discharged in the related art, because the pressure regulating cavity does not need to be adjusted. In the embodiment, the oil in the pressure regulating cavity needs to be discharged in order to maintain the pressure of the oil in the pressure regulating cavity, because the throttle has a certain adjusting effect on the pressure of the oil in the pressure regulating cavity. That is, when the outside continuously supplements the oil to the pressure regulating cavity, if the oil in the pressure regulating cavity cannot be discharged, the pressure of the oil in the pressure regulating cavity will eventually be the same as that of the continuously supplemented oil outside, so the throttle cannot change the flow of the throttle by adjusting the pressure of the oil in the pressure regulating cavity. In the embodiment, the third throttling channel 1216 is provided, so that the oil in the pressure regulating cavity can be discharged, and the problem that the pressure of the oil in the pressure regulating cavity is eventually increased due to the continuous supplement of the oil to the pressure regulating cavity is avoided. On the other hand, the minimum cross-sectional area of the third throttling channel 1216 is smaller than that of the overflow channel 130, and the third throttling channel 1216 has a throttling effect, so as to avoid that the amount of oil flowing out through the third throttling channel 1216 is too much, and the oil in the pressure regulating cavity is discharged through the third throttling channel 1216. In some embodiments, the third throttling channel 1216 is a capillary channel.

[0062] Further, the first groove 1211 is provided with a throttling boss 12111 in the center, and the throttling boss 12111 is provided with a first channel 1215. The diaphragm 14 and the space in the first groove 1211 outside the throttling boss 12111 form a pressure stabilizing cavity.

[0063] Specifically, when there is no load on the static pressure cavity, the diaphragm 14 abuts against the throttling boss 12111 and closes the first channel 1215. At this time, the oil in the pressure stabilizing cavity cannot flow into the static pressure cavity through the first channel 1215. When the load on the static pressure cavity is large, the oil in the static pressure cavity has a certain pressure and is transmitted to the first channel 1215, so that the oil in the first channel 1215 exerts a pressure on the diaphragm 14, causing the diaphragm 14 to deform or sag away from the throttling boss 12111. At this time, the diaphragm 14 opens the first channel 1215, and the oil in the pressure stabilizing cavity can enter the static pressure cavity through the first channel 1215, thereby increasing the flow of the oil out of the throttle and improving the rigidity of the oil in the static pressure cavity and the load-carrying capacity of the static pressure cavity.

[0064] Further, the rotating body 13 is provided with a spiral groove 1311 on the side close to the diaphragm 14. The center of the spiral groove 1311 is located on the axis of the rotating body 13, and the spiral groove 1311 communicates with the pressure regulating cavity.

[0065] Specifically, the rotating body 13 is inserted into the first groove 1211 and abuts against the diaphragm 14, and a pressure regulating cavity is formed between the diaphragm 14 and the spiral groove 1311. In this embodiment, the spiral groove 1311 is arranged such that the oil liquid in the spiral groove 1311 exerts more uniform pressure on the diaphragm 14, avoiding damage to the diaphragm 14 caused by uneven force on different parts of the diaphragm 14, and thus improving the service life of the flow restrictor to some extent.

[0066] In some embodiments, a bearing boss 12112 is further arranged in the first groove 1211, and the bearing boss 12112 is used to support the diaphragm 14 and has the same height as the throttling boss 12111. Specifically, the bearing boss 12112 is arranged outside the throttling boss 12111 and is used to support the diaphragm 14, avoiding damage to the diaphragm 14 caused by excessive hydraulic pressure in the pressure regulating cavity. The bearing boss 12112 has the same height as the throttling boss 12111, so that the bearing boss 12112 and the throttling boss 12111 provide more uniform support to the diaphragm 14.

[0067] To verify the effect of the flow restrictor of the present application, some specific embodiments are provided in the present application:

[0068] Comparative Example 1: The angle of the central angle A formed between the line connecting the first end of the overflow channel 130 to the rotation center of the rotating body 13 and the line connecting the first opening 12121 to the rotation center of the rotating body 13 is 0, and the rotation angle of the rotating body 13 is 0, which is used to simulate the second throttling channel 1214 directly communicating with the pressure stabilizing cavity in the related art, and the load force on the static pressure cavity is 0.1 Mpa. At this time, the flow rate of the oil liquid flowing into the static pressure cavity through the first channel 1215 of the flow restrictor is 63 ml / min.

[0069] Example 1: Different from Comparative Example 1, the angle of the central angle A is 45°, and at this time, the flow rate of the oil liquid flowing into the static pressure cavity through the first channel 1215 of the flow restrictor is 87 ml / min.

[0070] Example 2: Different from Comparative Example 1, the angle of the central angle A is 90°, and at this time, the flow rate of the oil liquid flowing into the static pressure cavity through the first channel 1215 of the flow restrictor is 102 ml / min.

[0071] Comparative Example 2: Different from Comparative Example 1, the load force on the static pressure cavity is 0.3 Mpa, and at this time, the flow rate of the oil liquid flowing into the static pressure cavity through the first channel 1215 of the flow restrictor is 67 ml / min.

[0072] Example 3: Different from Comparative Example 2, the angle of the central angle A is 45°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 91 ml / min.

[0073] Example 4: Different from Comparative Example 2, the angle of the central angle A is 90°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 106 ml / min.

[0074] Comparative Example 3: Different from Comparative Example 1, the load force borne by the static pressure cavity is 0.6 Mpa, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 74 ml / min.

[0075] Example 5: Different from Comparative Example 3, the angle of the central angle A is 45°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 97 ml / min.

[0076] Example 6: Different from Comparative Example 3, the angle of the central angle A is 90°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 114 ml / min.

[0077] Comparative Example 4: Different from Comparative Example 1, the load force borne by the static pressure cavity is 0.9 Mpa, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 80 ml / min.

[0078] Example 7: Different from Comparative Example 4, the angle of the central angle A is 45°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 104 ml / min.

[0079] Example 8: Different from Comparative Example 4, the angle of the central angle A is 90°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 120 ml / min.

[0080] Comparative Example 5: Different from Comparative Example 1, the load force borne by the static pressure cavity is 1.3 Mpa, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 90 ml / min.

[0081] Example 9: Different from Comparative Example 5, the angle of the central angle A is 45°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 112 ml / min.

[0082] Example 10: Different from Comparative Example 5, the angle of the central angle A is 90°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 130 ml / min.

[0083] Comparative Example 6: Different from Comparative Example 1, the load force on the static pressure cavity is 1.8 MPa, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the restrictor is 99 ml / min.

[0084] Example 11: Different from Comparative Example 6, the angle of the central angle A is 45°, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the restrictor is 122 ml / min.

[0085] Example 12: Different from Comparative Example 6, the angle of the central angle A is 90°, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the restrictor is 140 ml / min.

[0086] Comparative Example 7: Different from Comparative Example 1, the load force on the static pressure cavity is 2.2 MPa, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the restrictor is 105 ml / min.

[0087] Example 13: Different from Comparative Example 7, the angle of the central angle A is 45°, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the restrictor is 127 ml / min.

[0088] Example 14: Different from Comparative Example 7, the angle of the central angle A is 90°, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the restrictor is 144 ml / min.

[0089] Comparative Example 8: Different from Comparative Example 1, the load force on the static pressure cavity is 2.5 MPa, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the restrictor is 102 ml / min.

[0090] Example 15: Different from Comparative Example 8, the angle of the central angle A is 45°, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the restrictor is 122 ml / min.

[0091] Example 16: Different from Comparative Example 8, the angle of the central angle A is 90°, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the restrictor is 132 ml / min.

[0092] Comparative Example 9: Different from Comparative Example 1, the load force on the static pressure cavity is 2.7 MPa, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the restrictor is 91 ml / min.

[0093] Example 17: Different from Comparative Example 9, the angle of the circle center angle A is 45°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 93 ml / min.

[0094] Example 18: Different from Comparative Example 9, the angle of the circle center angle A is 90°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 105 ml / min.

[0095] Comparative Example 10: Different from Comparative Example 1, the load force borne by the static pressure cavity is 2.8 Mpa, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 75 ml / min.

[0096] Example 19: Different from Comparative Example 10, the angle of the circle center angle A is 45°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 82 ml / min.

[0097] Example 20: Different from Comparative Example 10, the angle of the circle center angle A is 90°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 82 ml / min.

[0098] Comparative Example 11: Different from Comparative Example 1, the load force borne by the static pressure cavity is 3.0 Mpa, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 43 ml / min.

[0099] Example 21: Different from Comparative Example 11, the angle of the circle center angle A is 45°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 41 ml / min.

[0100] Example 22: Different from Comparative Example 11, the angle of the circle center angle A is 90°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 48 ml / min.

[0101] Comparative Example 12: Different from Comparative Example 1, the load force borne by the static pressure cavity is 3.2 Mpa, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 0 ml / min.

[0102] Example 23: Different from Comparative Example 12, the angle of the circle center angle A is 45°, and the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 0 ml / min.

[0103] Example 24: Different from Comparative Example 12, the angle of the central angle A is 90°, at this time the flow rate of the oil flowing into the static pressure cavity through the first passage 1215 of the flow restrictor is 0 ml / min.

[0104] Table 1:

[0105]

[0106] According to the above comparative examples, examples, table 1 and the attached Figure 10 It can be known that when the pressure borne by the static pressure cavity is between 0.1 Mpa and 2.2 Mpa, the flow rate of the flow restrictor increases as the pressure borne by the static pressure cavity increases, which is due to the fact that the increase of the oil pressure makes the oil in the first passage 1215 exert an external force on the diaphragm 14, causing the diaphragm 14 to deform or protrude in a direction away from the throttling boss 12111, and the greater the pressure borne by the static pressure cavity, the higher the degree of deformation or protrusion of the diaphragm 14, thereby making the oil in the stable pressure cavity more easily enter the static pressure cavity through the first passage 1215. When the pressure borne by the static pressure cavity is between 2.2 Mpa and 3.2 Mpa, the pressure borne by the static pressure cavity is relatively large, causing the pressure of the oil in the first passage 1215 to have a certain hindering effect on the oil in the first throttling passage 1213, ultimately making it more difficult for the external oil to enter the flow restrictor, thereby causing the flow rate of the flow restrictor to decrease. It is worth mentioning that the maximum pressure of the oil provided by the static pressure device of the present application to the flow restrictor is 3.2 Mpa, so when the load borne by the static pressure cavity is 3.2 Mpa, the oil in the flow restrictor remains static under the action of the oil inlet pressure and the oil return pressure of the static pressure cavity, so at this time the flow rate of the flow restrictor is 0. In addition, according to table 1 and the attached Figure 10 It can be known that when the pressure borne by the static pressure cavity is between 0.1 Mpa and 2.2 Mpa, the flow rate of the flow restrictor increases as the pressure borne by the static pressure cavity increases, which is due to the fact that the increase of the oil pressure makes the oil in the first passage 1215 exert an external force on the diaphragm 14, causing the diaphragm 14 to deform or protrude in a direction away from the throttling boss 12111, and the greater the pressure borne by the static pressure cavity, the higher the degree of deformation or protrusion of the diaphragm 14, thereby making the oil in the stable pressure cavity more easily enter the static pressure cavity through the first passage 1215. When the pressure borne by the static pressure cavity is between 2.2 Mpa and 3.2 Mpa, the pressure borne by the static pressure cavity is relatively large, causing the pressure of the oil in the first passage 1215 to have a certain hindering effect on the oil in the first throttling passage 1213, ultimately making it more difficult for the external oil to enter the flow restrictor, thereby causing the flow rate of the flow restrictor to decrease. It is worth mentioning that the maximum pressure of the oil provided by the static pressure device of the present application to the flow restrictor is 3.2 Mpa, so when the load borne by the static pressure cavity is 3.2 Mpa, the oil in the flow restrictor remains static under the action of the oil inlet pressure and the oil return pressure of the static pressure cavity, so at this time the flow rate of the flow restrictor is 0. In addition, according to table 1 and the attached

[0107] In summary, the flow restrictor and the static pressure device of the present application have at least the following beneficial technical effects:

[0108] (1) Through the setting of the rotating body 13, the second channel 123, the first opening 12121 and the overflow channel 130, the distance between the first opening 12121 and the first end of the overflow channel 130 can be adjusted by rotating the rotating body 13, so as to change the pressure of the oil liquid entering the pressure regulating cavity, and finally improve the flow regulating range of the flow regulator and the adaptability of the flow regulator.

[0109] (2) The rotating body 13 is directly rotated by the operator through the setting of the avoiding through hole 111 on the cover plate 11, the boss 132 on the rotating body 13 and the rotating part 1321 on the boss 132, that is, the cover plate 11 does not need to be disassembled, and the operation is convenient. In addition, the boss 132 is partially arranged in the avoiding through hole 111, that is, the cover plate 11 has a certain limiting effect on the boss 132 at this time, so as to avoid the deflection of the rotating body 13 when rotating, and improve the stability of the flow regulator.

[0110] (3) The rotating body 13 is provided with an identification part 1322, which is used to identify the position of the overflow channel 130, and the operator can know the angle between the first end of the overflow channel 130 and the first opening 12121 through the identification part 1322.

[0111] For the convenience of description, spatial relative terms such as "above", "upper", "on", "upper surface", "upper", etc. can be used herein to describe the spatial positional relationship of one device or feature with other devices or features as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the device described in the drawings. For example, if the device in the drawing is inverted, the device described as "above" or "above" other devices or structures will be positioned "below" or "below" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative description used herein is interpreted accordingly.

[0112] In addition, it should be noted that the use of "first", "second" and the like to define parts is only for the convenience of distinguishing the corresponding parts, and the above words have no special meaning unless otherwise stated, and therefore cannot be understood as limiting the scope of protection of the present application.

[0113] The above is only a preferred embodiment of the present application and is not intended to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present application shall be included in the protection scope of the present application.

Claims

1. A flow restrictor characterized by, The utility model relates to a pressure regulating device, which comprises: a base (12) having a first side (121) and a second side (122) arranged oppositely, the first side (121) of the base (12) is provided with a first recess (1211), the first recess (1211) is provided with a first channel (1215) therein, the first channel (1215) extends from the first side (121) to the second side (122), the second side (122) of the base (12) is provided with a recess (1221) for forming an oil supply channel with a predetermined device, the base (12) is further provided with an oil supply port (1222), a first throttling channel (1213) and a second throttling channel (1214), the oil supply port (1222) is in communication with the oil supply channel and the second throttling channel (1214), the first end of the second throttling channel (1214) extends to the first side (121), and the second end of the second throttling channel (1214) extends to the second side (122); a diaphragm (14) arranged in the first recess (1211) and forming a pressure stabilizing cavity with the first recess (1211); a rotating body (13) provided with an overflow channel (130), the rotating body (13) is at least partially rotatably arranged in the first recess (1211) and located on the side of the diaphragm (14) away from the bottom of the first recess (1211), the rotating body (13) and the diaphragm (14) form a pressure regulating cavity therebetween, the rotating body (13) and the base (12) are provided with a second channel (123), the second channel (123) is provided with a first opening (12121), the first opening (12121) is in communication with the first end of the second throttling channel (1214) and the first opening (12121), the first end of the overflow channel (130) is in communication with the second channel (123), the second end of the overflow channel (130) is in communication with the pressure regulating cavity, and the rotating body (13) rotates to increase or decrease the distance between the first opening (12121) and the first end of the overflow channel (130); a cover plate (11) covering the first side (121) and the rotating body (13); wherein the two ends of the first throttling channel (1213) are in communication with the oil supply channel and the pressure stabilizing cavity respectively, the second end of the second throttling channel (1214) is in communication with the oil supply channel, and the first channel (1215) is in communication with the static pressure cavity of the predetermined device and the oil supply channel.

2. The flow restrictor of claim 1, wherein The first side (121) is further provided with a second recess (1212) located at the outer periphery of the first recess (1211), and the first opening (12121) is arranged in the second recess (1212). The rotating body (13) is overlapped with the second groove (1212) and forms the second channel (123) with the second groove (1212).

3. The flow restrictor of claim 2, wherein The rotating body (13) has an outer flange (131) which protrudes from the rotating body (13) in a direction away from the rotation center of the rotating body (13) and is located outside the first groove (1211), the outer flange (131) is overlapped with the second groove (1212), and the overflow channel (130) is arranged between the rotating body (13) and the outer flange (131).

4. The flow restrictor of claim 3, wherein The outer flange (131) is provided with a first overflow groove (1301) on one side close to the second groove (1212), the first overflow groove (1301) is communicated with the second groove (1212), the outer circumferential surface of the rotating body (13) in the first groove (1211) is provided with a second overflow groove (1302) communicated with the first overflow groove (1301), and the first overflow groove (1301) and the second overflow groove (1302) form the overflow channel (130).

5. The flow restrictor of claim 2, wherein The first groove (1211) comprises a circular groove, and the second groove (1212) comprises a circular ring groove coaxially arranged with the circular groove. The rotating body (13) comprises a circular rotating body which rotates around the axis of the circular groove under the action of an external force.

6. The flow restrictor of any one of claims 1 to 5, wherein, The cover plate (11) is provided with a relief through hole (111) extending in the height direction of the flow regulator, the rotating body (13) is provided with a boss (132) on the side away from the base (12), the boss (132) is at least partially located in the relief through hole (111), and the boss (132) is provided with a rotating part (1321) on the side away from the base (12).

7. The flow restrictor of any one of claims 1 to 5, wherein, The overflow channel (130) is arranged on the side wall surface of the rotating body (13), the rotating body (13) is provided with an identification part (1322) on the side away from the first groove (1211), and in the projection of the flow regulator in the height direction, the projection of the identification part (1322) and the projection of the overflow channel (130) are located on the same straight line from the geometric center of the projection surface of the rotating body (13) to the outside of the rotating body (13).

8. The flow restrictor of any one of claims 1 to 5, wherein, The base (12) is provided with a third throttling channel (1216), the first end of the third throttling channel (1216) extends to the pressure regulating cavity, the second end of the third throttling channel (1216) extends to the second side (122), and the minimum cross-sectional area of the third throttling channel (1216) is smaller than the minimum cross-sectional area of the overflow channel (130).

9. The flow restrictor of any one of claims 1 to 5, wherein, The first recess (1211) is centrally provided with a throttling boss (12111) having the first passage (1215) formed therein, and the diaphragm (14) and a space in the first recess (1211) outside the throttling boss (12111) form the pressure stabilizing chamber; and / or, The rotating body (13) is provided on one side close to the diaphragm (14) with a spiral groove (1311) having a center on the axis of the rotating body (13), and the spiral groove (1311) is in communication with the pressure regulating chamber.

10. A hydrostatic device, characterized by The static pressure device comprises the throttling device according to any one of claims 1 to 9.

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