CN115839357B - Delay brake control valve for hydraulic rotary motor - Google Patents
Delay brake control valve for hydraulic rotary motor Download PDFInfo
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- CN115839357B CN115839357B CN202310107732.XA CN202310107732A CN115839357B CN 115839357 B CN115839357 B CN 115839357B CN 202310107732 A CN202310107732 A CN 202310107732A CN 115839357 B CN115839357 B CN 115839357B
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- 239000003921 oil Substances 0.000 claims description 160
- 239000010720 hydraulic oil Substances 0.000 claims description 22
- 238000004891 communication Methods 0.000 claims description 4
- 238000001514 detection method Methods 0.000 abstract description 8
- 230000000694 effects Effects 0.000 abstract description 6
- 230000009471 action Effects 0.000 description 5
- 238000009530 blood pressure measurement Methods 0.000 description 4
- 238000009434 installation Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 230000003111 delayed effect Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 239000002245 particle Substances 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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Abstract
The invention discloses a time-delay braking control valve for a hydraulic rotary motor, wherein a first valve core hole and a second valve core hole are respectively and horizontally penetrated through a valve body of the control valve, and a pilot valve core capable of moving along the axial direction is arranged in the first valve core hole; a throttling valve core and a pressure measuring valve core which can move along the axial direction are arranged in the second valve core hole; the two ends of the first valve core hole and the second valve core hole are plugged, and a first oil way and a second oil way which are respectively communicated with different positions of the first valve core hole and the second valve core hole are also arranged in the valve body; the outer wall of the valve body is also provided with a normal oil supply path, a pilot oil path, a brake release oil path and an oil return path, and the periphery of the pilot valve core is provided with a first annular groove corresponding to the brake release oil path and the normal oil supply path; the outer wall of the valve body at the side face of the pressure measuring valve core is provided with a pressure detecting hole and a pressure measuring plug, and a channel communicated with the second oil way and the pressure detecting hole is arranged in the pressure measuring valve core. The time delay brake control valve is convenient for pressure detection of a brake controller control cavity and has good time delay effect.
Description
Technical Field
The invention relates to the technical field of hydraulic pressure, in particular to a delay brake control valve for a hydraulic rotary motor.
Background
The existing hydraulic rotary motor has the requirement of braking delay in application so as to avoid the problem of transitional wear of a brake pad and a stop ring in emergency braking, so that a delay braking control valve gradually appears in the market. The existing delay brake control valve mainly has two functions, namely, braking release in a hydraulic rotary motor and braking delay.
However, in actual application, there is a need to detect the pressure condition in the spring brake control chamber of the swing motor at the time of braking or releasing braking, but the structure of the current time-lapse brake control valve is difficult to meet the need, and a pressure detection port for detecting the pressure value of the spring brake control chamber at the time of releasing braking and time-lapse braking is lacking.
Thus, the prior art is still to be further developed.
Disclosure of Invention
Aiming at the technical problems, the invention provides a time-delay brake control valve for a hydraulic rotary motor, which realizes the operability and convenience of pressure detection of a brake controller control cavity through the improvement of the internal structure of a valve body and the addition of a pressure measuring valve core and a pressure detecting port.
In order to solve the problems, the invention provides the following technical scheme:
a delay brake control valve for a hydraulic rotary motor is characterized in that a first valve core hole and a second valve core hole are respectively and horizontally penetrated through a valve body of the control valve, and a pilot valve core and a first reset spring which can move along the axial direction are arranged in the first valve core hole; a second reset spring, a throttling valve core and a pressure measuring valve core which can move along the axial direction are sequentially arranged in the second valve core hole; the two ends of the first valve core hole and the second valve core hole are plugged, and a first oil way and a second oil way which are respectively communicated with different positions of the first valve core hole and the second valve core hole are also arranged in the valve body; the outer wall of the valve body is also provided with a normal oil supply path, a pilot oil path, a brake release oil path and an oil return path, and the periphery of the pilot valve core is provided with a first annular groove corresponding to the brake release oil path and the normal oil supply path;
the outer wall of the valve body at the side surface of the pressure measuring valve core is provided with a pressure detecting hole, the pressure measuring plug is arranged on the pressure detecting hole, and a channel which is communicated with the second oil way and the pressure detecting hole is arranged in the pressure measuring valve core;
when the brake is released, the pilot valve core moves to a first working position, and the first annular groove corresponds to the normal oil supply passage and the brake release oil passage at the same time, so that the communication between the normal oil supply passage and the brake release oil passage is realized;
during braking, the pilot valve core returns to the second working position, the first annular groove is staggered from the normal oil supply path, the first annular groove only corresponds to the braking releasing oil path, and the braking releasing oil path, the first annular groove, the second oil path, the second valve core hole, the first oil path, the second valve core hole and the oil return oil path are mutually communicated.
Optionally, in the delay brake control valve, the outer diameter of the inner end of the pressure measuring valve core, which is close to the throttling valve core, is smaller than the inner diameter of the second valve core hole, and an annular gap is formed between the outer periphery of the inner end of the pressure measuring valve core and the inner wall of the second valve core hole.
Optionally, in the delay brake control valve, a first pressure measuring valve core hole communicated with the second oil way is arranged at the periphery of the pressure measuring valve core, a second pressure measuring valve core hole is arranged at the side wall of the pressure measuring valve core corresponding to the pressure detecting hole, and a third pressure measuring valve core hole communicated with the first pressure measuring valve core hole and the second pressure measuring valve core hole is arranged in the pressure measuring valve core.
Preferably, the pressure measuring valve core is further provided with a second annular groove corresponding to the periphery of the second oil path, and the first pressure measuring valve core hole is positioned on the inner wall of the second annular groove.
Optionally, in the delay brake control valve, two ends of the first valve core hole and the second valve core hole are respectively provided with a first plug, the first return spring is arranged between one end of the pilot valve core and the adjacent first plug, a first pilot cavity is enclosed between one end of the pilot valve core, which is far away from the first return spring, and the adjacent first plug, and a second pilot cavity is enclosed between the pilot valve core, which is close to the first return spring, and the inner wall of the first valve core hole; the first pilot cavity is communicated with the pilot oil path;
the lower end of the first oil way is communicated with a second pilot cavity, the upper end of the first oil way is communicated with the inner side wall of a second valve core hole where the throttle valve core is positioned, and one end of the second oil way is communicated with a first annular groove of the first valve core hole; the inner end of the braking relieving oil way is communicated with the first annular groove, and the inner end of the oil return oil way is communicated with the second pilot cavity.
Optionally, in the delay brake control valve, a spring cavity is formed in the end face, away from the pressure measuring valve core, of the throttle valve core in an inward axial direction, and a second reset spring is arranged in the spring cavity in the axial direction; the side wall of the spring cavity is provided with a slotted hole used for communicating the first oil way; one end of the throttle valve core, which is close to the pressure measuring valve core, is provided with a throttle small hole, and the inner end of the throttle small hole is communicated with the spring cavity.
Optionally, in the delay brake control valve, the end face of the throttle valve core, which is close to the pressure measuring valve core, is sunken to form a sinking groove, and the throttle small hole is arranged on the bottom wall of the sinking groove; the inner diameter of the throttling small hole is smaller than the inner diameter of the bottom of the sinking tank.
Optionally, in the delay brake control valve, a third annular groove is further arranged in the middle of the throttle valve core along the circumferential direction, a second throttle valve core hole communicated with the spring cavity is formed in the inner wall of the third annular groove, the side wall, close to the first oil duct, of the third annular groove is provided with a protruding ring, and a throttle gap is formed between the protruding ring and the inner wall of the second valve core hole.
Preferably, a fourth annular groove is further formed in one side, close to the first oil duct, of the protruding ring.
When the throttle valve core is positioned at the first position, the fourth annular groove corresponds to the first oil duct, the third annular groove is staggered with the first oil duct, hydraulic oil in the spring cavity flows out of the third annular groove and flows to the fourth annular groove and the first oil duct along the throttle gap, and in the process, the throttle gap realizes the second throttle effect;
when the throttle valve core is positioned at the second position, the third annular groove corresponds to the first oil duct in position, and hydraulic oil in the spring cavity directly flows from the third annular groove to the first oil duct.
Optionally, in the delay brake control valve, a pressure equalizing groove is arranged on the side wall of the throttle valve core, which is close to the sinking groove, along the circumferential direction, a first throttle valve core hole is arranged in the throttle valve core, and the pressure equalizing groove is communicated with the sinking groove through the first throttle valve core hole.
When hydraulic oil passes through the throttle valve core, the hydraulic oil can enter the equalizing groove through the first throttle valve core hole, and the phenomenon of locking of the throttle valve core is prevented.
Optionally, in the delay brake control valve, one end of the pilot valve core forms a spring mounting column, and one end of the first return spring is sleeved on the spring mounting column.
Optionally, in the delay brake control valve, a side wall of one end of the pressure measuring valve core, which is far away from the throttle valve core, is provided with a limiting protrusion, and a position of the second valve core hole, which corresponds to the limiting protrusion, is provided with a limiting boss matched with the limiting protrusion.
The limiting boss prevents the pressure measuring valve core from approaching the throttling valve core, and ensures the normal operation of the throttling valve core. Preferably, the limit protrusion is a limit head formed by radial expansion of the end part of the pressure measuring valve core.
The delay braking control valve for the hydraulic rotary motor has the following beneficial effects:
1. through the improvement of the internal structure of the valve body and the addition of the pressure measuring valve core and the pressure detecting port, the operability and convenience of pressure detection of a control cavity of the brake controller are realized. When the pressure sensor is applied, the pressure sensor is connected with the plug at the pressure detection port after the plug is removed, and then the pressure in the control cavity of the spring brake can be detected by the connected acquisition instrument when the rotary motor releases the brake or brakes.
2. Based on the pressure change of the control cavity of the detectable brake controller, the pressure change in the control cavity of the brake collected from the pressure detection port can be further analyzed, the contact area of the pressure in the control cavity of the brake multiplied by the oil is the pressure (F1) in the control cavity of the brake, and the pressure is compared with the total elastic force (F2) of the integral brake spring of the motor, so that the time delay of braking and releasing the brake of the time delay brake control valve is calculated.
3. The oil way of the delay brake control valve is skillfully designed, so that the hydraulic oil in the control cavity of the brake controller is throttled twice during oil return, and a good brake delay effect is achieved on the rotary motor, thereby avoiding excessive wear of the brake pad and the brake ring, and reducing pollution of wear particles and dirt of the brake pad on the rubber surface to the hydraulic oil.
Drawings
FIG. 1 is a schematic view showing the overall structure of a time delay brake control valve in embodiment 1 of the present invention;
FIG. 2 (1) is a side view of a time delay brake control valve; FIG. 2 (2) is a front view of the time delay brake control valve;
FIG. 3 is a B-B cross-sectional view of the time delay brake control valve of FIG. 2 (1) in an operational state;
FIG. 4 is a cross-sectional view A-A of the time delay brake control valve of FIG. 3 in an operational state;
FIG. 5A is a B-B cross-sectional view of the time delay brake control valve in operating condition two; FIG. 5B is a cross-sectional view of the time delay brake control valve in operating condition two;
FIG. 6 is an enlarged schematic view of the structure of FIG. 3A;
FIG. 7 is a schematic diagram of a mechanism of a pressure measurement valve cartridge;
FIG. 8 is a schematic view of a partially cut-away perspective view of a time delay brake control valve;
wherein reference numerals are as follows:
1. the brake system includes a rotary motor, 2, a brake assembly, 21, a brake ring, 22, a brake pad, 3, a spring brake, 31, a control chamber, 32, a brake spring, 4, a valve body, 41, a brake release oil passage, 42, an oil return oil passage, 43, a first oil passage, 44, a common oil passage, 45, a second oil passage, 46, a pilot oil passage, 47, a first spool bore, a first pilot chamber 47a, a second pilot chamber 47b, 48, a second spool bore, a 5.O type seal ring, 6, a first plug, 7, a first return spring, 8, a pilot spool, 81, a first annular groove, 9, a pressure spool, 91, a first pressure spool bore, 92, a second spool bore, 93, a third pressure spool bore, 94, an annular gap, 95, a second annular groove, 10, a pressure spool, 11, a double-ended plug, 12, a throttle spool, 121, a pressure equalizing groove, 122, a first throttle orifice, 124, a spring chamber 125, a second throttle spool bore, 126, a throttle gap, 127, a sink fourth annular groove, 128, and a third annular groove 129. 13. A second return spring, 14. A spring seat.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to fall within the scope of the invention. It will be understood that when an element is referred to as being "fixed" to another element, it can be directly on the other element or one or more intervening elements may be present therebetween. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or one or more intervening elements may be present therebetween. The terms "vertical," "horizontal," "left," "right," "upper," "lower," "inner," "outer," "bottom," and the like as used in this specification are based on the orientation or positional relationship shown in the drawings, merely to facilitate description of the invention and to simplify the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the invention. Furthermore, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used in the description of the invention herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and/or" as used in this specification includes any and all combinations of one or more of the associated listed items. In addition, the technical features of the different embodiments of the present invention described below may be combined with each other as long as they do not collide with each other.
Example 1
As shown in fig. 1 to 5 and 8, the present embodiment provides a time-lapse brake control valve for a hydraulic swing motor, which is mainly used for brake release and time-lapse braking of the swing hydraulic motor.
Specifically, as shown in fig. 3 to 5, a first spool hole 47 and a second spool hole 48 are horizontally provided in the valve body 4 of the control valve, and a pilot spool 8 and a first return spring 7 that can reciprocate linearly in the axial direction are provided in the first spool hole 47. A second return spring 13, a throttle valve core 12 which can move along the axial direction and a pressure measuring valve core 9 are sequentially arranged in the second valve core hole 48. Both ends of the first valve core hole and the second valve core hole are in plugging arrangement. The diameter of the first valve core hole is matched with that of the pilot valve core, and the hole surface of the first valve core hole is attached to the pilot valve core and is in sliding connection with the pilot valve core. The diameter of the second valve core hole is matched with the diameter of the throttle valve core, and the hole surface of the second valve core hole is attached to the throttle valve core and is in sliding connection with the throttle valve core.
Specifically, both ends of the first spool hole and the second spool hole may be plugged by installing the first plug 6. In the embodiment, the first plug 6 is a G1/4 plug and is sealed by an O-shaped sealing ring. In other embodiments, the first plug may be fastened to the valve body by fastening.
One end of the first return spring 7 acts on the pilot valve core, so that the pilot valve core can automatically return when no hydraulic pressure exists in the valve body, and one end of the pilot valve core, which is far away from the first return spring, is a pressure sensing end and is close to a subsequent pilot oil path 46. One end of the second return spring 13 acts on the throttle valve core 12, so that the throttle valve core can automatically return when the second valve core hole is not subjected to hydraulic pressure.
The valve body is also provided with a first oil path 43 and a second oil path 45 which are respectively communicated with different positions of the first valve core hole 47 and the second valve core hole 48. Based on processing reasons, the first oil way and the second oil way of the embodiment extend to the outer wall of the valve body after penetrating through the second valve core hole to form an opening, and the opening is plugged by installing a double-head plug to keep the sealing of the first oil way and the second oil way.
As shown in fig. 3 to 4, the outer wall of the valve body is further provided with a normal oil supply passage 44, a pilot oil passage 46, a brake release oil passage 41 and an oil return oil passage 42, the pilot oil passage 46, the brake release oil passage 41 and the normal oil supply passage 44 are all communicated with the first valve core hole, as shown in fig. 4, the brake release oil passage 41 is used for being connected with the control chamber 31 of the spring brake, and the outer periphery of the pilot valve core is provided with a first annular groove 81 corresponding to the brake release oil passage 41 and the normal oil supply passage 44.
The end, far away from the first return spring, of the pilot valve core 8 and the adjacent first plug enclose a first pilot cavity 47a, and the end, close to the first return spring, of the pilot valve core 8 and the adjacent first plug and the inner wall of the first valve core hole enclose a second pilot cavity 47b; the first pilot chamber 47a communicates with the pilot oil passage 46.
The first pilot chamber 47a is a pressure sensing chamber, when the first pilot chamber 47a receives pressure from the pilot oil path, the pilot valve core is pushed to do linear motion in the direction of the first return spring, the first return spring is compressed until the pilot valve core moves to the first working position, and the first annular groove 81 is correspondingly communicated with the normal oil path 44 and the brake release oil path 41 at the same time, so that communication between the normal oil path 44 and the brake release oil path 41 is realized, and at the moment, hydraulic oil introduced by the normal oil path can flow into a control chamber of the spring brake through the annular groove and the brake release oil path, so that the spring brake releases a brake state.
When the first pilot chamber 47a releases the pressure, the pilot spool returns to the second operating position by the restoring force of the first restoring spring, the first annular groove 81 is displaced from the normal oil passage 44, the first annular groove 81 corresponds only to the brake release oil passage 41, and the brake release oil passage 41, the first annular groove 88, the second oil passage 45, the second spool hole 48, the first oil passage 43, the second spool hole, and the return oil passage 42 communicate with each other.
Through the above-mentioned structure setting of delay brake control valve make it have the function that brakes and release and delay brake, on this basis, the pressure in order to be convenient for detect rotary motor's brake controller control chamber of this application is provided with the pressure measurement case in the second case hole of delay brake control valve of this application, and the concrete setting of pressure measurement case and relevant structure is as follows:
pressure measuring valve core
In order to facilitate detection of the pressure in the brake controller control chamber of the swing motor, a pressure measuring valve core 48 is provided in the second core hole of the time delay brake control valve of the present application. Specifically, as shown in fig. 3 and 7, a pressure detecting hole 10a is provided in the outer wall of the valve body at the side of the pressure detecting valve core 48, the pressure detecting plug 10 is mounted on the pressure detecting hole, and a channel for communicating the second oil path 45 with the pressure detecting hole is provided in the pressure detecting valve core 48. The pressure measuring plug and the pressure detecting hole are connected in a detachable mode such as a screw connection mode or a clamping connection mode.
Specifically, in this embodiment, the pressure measuring plug 10 is screwed with a pressure detecting hole with internal threads by using a plug (e.g., ZG1/8 plug). Because the double-head plug and the ZG1/8 plug are provided with the conical thread structure, the sealing ring is not required to be arranged through the threaded connection of the conical thread and the corresponding installation part of the valve block, the space is saved, the installation is convenient and quick, and the fixation firmness is higher.
The end of the second valve core hole, which is positioned at the pressure measuring plug end, is a pressure measuring end, the outer diameter of the inner end of the pressure measuring valve core 9, which is close to the throttle valve core 12, is smaller than the inner diameter of the second valve core hole 48, and an annular gap 94 is formed between the outer periphery of the inner end of the pressure measuring valve core 9 and the inner wall of the second valve core hole. The hydraulic oil from the second oil passage flows to the throttle valve core 8 along the annular gap, flows into the first oil passage after being throttled by the throttle valve core 8, and flows to the return oil passage along the second pilot chamber 47b of the second valve core hole.
Further specifically, a first pressure measuring valve core hole 91 communicated with the second oil path is arranged at the periphery of the pressure measuring valve core 9, a second pressure measuring valve core hole 92 is arranged on the side wall of the pressure measuring valve core corresponding to the pressure detecting hole 10a, and a third pressure measuring valve core hole 93 communicated with the first pressure measuring valve core hole 91 and the second pressure measuring valve core hole 92 is arranged in the pressure measuring valve core. In this embodiment, the pressure measuring valve core 9 is further provided with a second annular groove 95 corresponding to the outer periphery of the second oil path, and the first pressure measuring valve core hole 91 is located on the inner wall of the second annular groove.
Through the above arrangement, the pressure detecting hole 10a is communicated with the brake release oil passage through the second pressure detecting valve core hole, the third pressure detecting valve core hole, the first pressure detecting valve core hole, the second oil passage and the first valve core hole 47, that is, the communication between the pressure detecting hole 10a and the control chamber of the spring brake is realized, so that the pressure of the control chamber of the spring brake can be obtained only through the pressure detection in the pressure detecting hole 10 a.
When the pressure is detected, only the pressure measuring plug on the pressure detecting hole is required to be removed, the pressure detecting hole is hermetically connected with a pressure sensor, and the acquisition instrument can detect the pressure in the spring brake control cavity when the rotary motor releases the brake or brakes through the pressure sensor; the pressure in the brake control cavity is acquired by the acquisition instrument and multiplied by the contact area of oil, namely the pressure (F1) in the brake control cavity, and the pressure is compared with the total elastic force (F2) of the motor integral brake spring; specifically, at motor braking delay: calculating and analyzing the duration from the time point when the pressure F1 is equal to F2 to the time point when F1 is smaller than F2, namely the duration is the braking delay time; therefore, based on the method, the time of delayed braking of the delayed braking control valve can be deduced by analyzing the collected change of the pressure in the brake control cavity.
In order to limit the pressure measuring valve core, the pressure measuring valve core is prevented from moving to contact the throttling valve core along the second valve core hole in the working process, normal working of the throttling valve core is prevented, and the following settings are carried out: the side wall of one end of the pressure measuring valve core, which is far away from the throttle valve core, is provided with a limiting protrusion 96, and the position of the second valve core hole, which corresponds to the limiting protrusion, is provided with a limiting boss matched with the limiting protrusion. The limiting boss prevents the pressure measuring valve core from approaching the throttling valve core, and ensures the normal operation of the throttling valve core. In this embodiment, the limiting protrusion is a limiting head formed by radially expanding the end of the pressure measuring valve core.
Example 2
On the basis of embodiment 1, in order to improve the braking delay (or throttling effect) of the delay braking control valve on the rotary motor, the following structure of the delay braking control valve of the embodiment is further improved:
pilot valve core
In this embodiment, as shown in fig. 3 to 8, a spring mounting post 81 is formed at one end of the pilot spool 8, and one end of the first return spring is fitted around the outer periphery of the spring mounting post. One end of the first return spring 7 acts on the pilot valve core, so that the pilot valve core can automatically return when no hydraulic pressure exists in the valve body, and the other end of the first return spring is connected with the adjacent first plug. In order to facilitate the installation of the first return spring, the first return spring is in contact with the adjacent first plug and the pilot valve core. Through setting up first reset spring, realize the automatic re-setting of guide's case, avoid increasing extra control oil circuit, simplified the oil circuit.
The lower end of the first oil way is communicated with the second pilot cavity 47b, the upper end of the first oil way is communicated with the inner side wall of a second valve core hole where the throttle valve core is positioned, and one end of the second oil way 45 is communicated with the first annular groove 81 of the first valve core hole 47; the inner end of the brake release oil passage 41 communicates with the first annular groove 81, and the inner end of the return oil passage 42 communicates with the second pilot chamber 47b.
The pilot valve core is matched with the adjacent first plug and used for limiting the linear movement distance when the first return spring drives the pilot valve core to return; meanwhile, the pressure measuring valve core is matched with the adjacent first plug and used for limiting the linear movement distance when the second return spring drives the throttling valve core to reset.
Throttle control of a throttle valve core
As shown in fig. 3 to 8, the end surface of the throttle valve core 12, which is far away from the pressure measuring valve core, is provided with a spring cavity 124 which is internally provided with a second return spring 13 along the axial direction. In this embodiment, a spring seat 14 is further disposed between the throttle valve core 12 and the adjacent first plug, the outer end of the second return spring is connected to the spring seat, and the inner end of the second return spring is connected to the inner wall of the spring cavity of the throttle valve core. In order to facilitate the installation of the second return spring, the second return spring is in contact with the throttle valve core and the spring seat.
When oil in the second oil way enters the second valve core hole, the throttling valve core can be pushed to do linear motion towards the direction of the second return spring, and the second return spring is compressed; when the oil pressure is smaller than the spring force of the second return spring or no oil exists, the return action of the second return spring drives the throttle valve core to return. Through setting up the second reset spring, realize the automatic re-setting of throttle case, avoid increasing extra control oil circuit, simplified the oil circuit.
The side wall of the spring cavity is provided with a slotted hole used for communicating the first oil way 43; the throttle valve core 12 is provided with the throttle aperture 123 near the one end of pressure measurement valve core, and the inner of throttle aperture communicates with spring chamber 124. Preferably, the end face of the throttle valve core 12 close to the pressure measuring valve core is sunken to form a sinking groove 128, and a throttle small hole is formed in the bottom wall of the sinking groove; the inner diameter of the throttling small hole is smaller than the inner diameter of the bottom of the sinking tank.
Because the throttle valve core contains the throttle small hole 123, the first throttle is generated when the hydraulic oil in the control cavity of the brake linkage device flows into the inner cavity of the motor of the shell, and the brake delay effect is achieved.
On the basis of the above, a third annular groove 129 is further formed in the middle of the throttle valve core along the circumferential direction, a second throttle valve core hole 125 communicated with the spring cavity is formed in the inner wall of the third annular groove, the side wall, close to the first oil duct, of the third annular groove 129 is provided with a protruding ring, a throttle gap 126 is formed between the protruding ring and the inner wall of the second valve core hole 48, and the protruding ring is in clearance fit with the inner wall of the second valve core hole. Preferably, a fourth annular groove 127 is further provided on the side of the protruding ring adjacent to the first oil passage.
When the pressure at the outer end of the throttling valve core is larger than the spring force of the second return spring, the second spring is in a compressed state, when the throttling valve core is located at the first position, the fourth annular groove 127 corresponds to the first oil duct 43 in position, the third annular groove 129 is staggered with the first oil duct 43 in position, and after the hydraulic oil subjected to the first throttling of the throttling small hole enters the spring cavity, the hydraulic oil flows out of the third annular groove 129 and flows to the fourth annular groove and the first oil duct along the throttling gap 126, and in the process, the throttling gap plays a second throttling role.
When the hydraulic pressure received by the pressure sensing end (namely, the end far away from the second return spring) of the throttle valve core is smaller than the elastic force of the second return spring or the second return spring is not stressed, the throttle valve core is reset to the second position under the action of the second return spring, the third annular groove 129 corresponds to the first oil duct in position, and hydraulic oil in the spring cavity directly flows from the third annular groove 129 to the first oil duct. In this state, the valve body realizes one throttle only through the throttle orifice.
Further, in order to prevent the choke valve core from being jammed, the following arrangement is performed: the side wall of the throttle valve core, which is close to the sinking groove 128, is provided with a pressure equalizing groove 121 along the circumferential direction, a first throttle valve core hole 122 is arranged in the throttle valve core 12, and the pressure equalizing groove is communicated with the sinking groove 128 through the first throttle valve core hole 122. When hydraulic oil passes through the throttle valve core, the hydraulic oil can enter the equalizing groove through the first throttle valve core hole, and the phenomenon of locking of the throttle valve core is prevented.
Working principle of brake delay and brake release of delay brake control valve
(1) Braking delay:
as shown in the hydraulic oil flows of (1) - (2) - (3) in fig. 3 and 4, when the hydraulic oil of the pilot oil path at the pressure sensing end of the pilot valve core is closed, the pilot valve core is reset under the action of the first reset spring, and meanwhile, the normal oil path 44 is cut off from being communicated with the control cavity 31 of the brake linkage through the annular groove of the pilot valve core, at the moment, under the action of the brake spring 32, the hydraulic oil in the control cavity 31 of the brake linkage can slowly return oil to the inner cavity of the motor shell through the brake release oil path 41, the second oil path 45, the annular gap 94, the throttle hole 123, the spring cavity 124, the second throttle valve core hole 125, the throttle gap 126, the annular groove 127, the first oil path 43 and the oil return oil path 42, so that not only is the braking of the rotary motor, but also the effect of braking delay is achieved through the throttle action, thereby avoiding excessive wear of a brake pad and a brake ring, and simultaneously reducing the pollution of wear particles of a rubber face brake pad to the hydraulic oil.
(2) Brake release:
as shown in the hydraulic oil flows from (1) to (2) to (3) of fig. 5 (a) and (B), when the first pilot chamber 47a receives the pressure from the pilot oil passage, the pilot spool is pushed to move linearly in the direction of the first return spring, the first return spring is compressed until the pilot spool moves to the first operating position, and the first annular groove 81 communicates with the normal oil passage 44 and the brake release oil passage 41 at the same time, so that the normal oil passage 44 and the brake release oil passage 41 communicate, and at this time, the hydraulic oil introduced from the normal oil passage can flow into the control chamber of the spring brake through the annular groove and the brake release oil passage, so that the spring brake releases the brake state.
The above embodiment 2 is a more optimized structure of the time delay brake control valve, and the detailed structure of the time delay brake control valve of the present application is not limited to embodiment 2, but equivalent substitutions or changes can be made by those skilled in the art based on the disclosure of the specification, and all such changes or substitutions shall fall within the scope of the appended claims.
Claims (8)
1. A time-delay brake control valve for a hydraulic rotary motor is characterized in that a first valve core hole (47) and a second valve core hole (48) are respectively and horizontally penetrated through a valve body (4), and a pilot valve core (8) capable of moving along the axial direction and a first return spring are arranged in the first valve core hole; a second return spring, a throttling valve core (12) capable of moving along the axial direction and a pressure measuring valve core (9) are sequentially arranged in the second valve core hole (48); the two ends of the first valve core hole and the second valve core hole are provided with plugging, and a first oil way (43) and a second oil way (45) which are respectively communicated with different positions of the first valve core hole (47) and the second valve core hole (48) are also arranged in the valve body; the outer wall of the valve body is also provided with a normal oil supply passage (44), a pilot oil passage (46), a brake release oil passage (41) and an oil return oil passage (42), and the periphery of the pilot valve core is provided with a first annular groove (81) corresponding to the brake release oil passage (41) and the normal oil supply passage (44); the outer wall of the valve body at the side surface of the pressure measuring valve core (9) is provided with a pressure detecting hole (10 a), the pressure measuring plug (10) is arranged on the pressure detecting hole, and a channel which is communicated with the second oil way (45) and the pressure detecting hole is arranged in the pressure measuring valve core (9);
the outer diameter of the inner end of the pressure measuring valve core (9) close to the throttling valve core (12) is smaller than the inner diameter of the second valve core hole (48), and an annular gap (94) is formed between the outer periphery of the inner end of the pressure measuring valve core (9) and the inner wall of the second valve core hole;
the periphery of the pressure measuring valve core (9) is provided with a first pressure measuring valve core hole (91) communicated with a second oil way, the side wall of the pressure measuring valve core corresponding to the pressure detecting hole (10 a) is provided with a second pressure measuring valve core hole (92), and a third pressure measuring valve core hole (93) communicated with the first pressure measuring valve core hole (91) and the second pressure measuring valve core hole (92) is arranged in the pressure measuring valve core;
when the brake is released, the pilot valve core moves to a first working position, and the first annular groove (81) corresponds to the normal oil supply path (44) and the brake release oil path (41) at the same time, so that the communication between the normal oil supply path (44) and the brake release oil path (41) is realized;
during braking, the pilot valve core returns to the second working position, the first annular groove is staggered from the normal oil supply path, the first annular groove only corresponds to the braking releasing oil path (41), and the braking releasing oil path (41), the first annular groove (88), the second oil path (45), the second valve core hole (48), the first oil path (43), the first valve core hole and the oil return oil path (42) are mutually communicated.
2. The time delay brake control valve for a hydraulic swing motor according to claim 1, wherein the pressure measuring valve core (9) is further provided with a second annular groove (95) corresponding to the outer periphery of the second oil passage, and the first pressure measuring valve core hole (91) is located at the inner wall of the second annular groove.
3. The time delay brake control valve for a hydraulic rotary motor according to claim 1, wherein first plugs (6) are respectively arranged at two ends of the first valve core hole and the second valve core hole, a first return spring (7) is arranged between one end of a pilot valve core (8) and the adjacent first plug, a first pilot cavity (47 a) is formed by enclosing between one end of the pilot valve core (8) far away from the first return spring and the adjacent first plug, and a second pilot cavity (47 b) is formed by enclosing between one end of the pilot valve core (8) near the first return spring and the adjacent first plug and the inner wall of the first valve core hole; the first pilot chamber (47 a) is communicated with a pilot oil path (46);
the lower end of the first oil way is communicated with a second pilot cavity (47 b), the upper end of the first oil way is communicated with the inner side wall of a second valve core hole where the throttle valve core is positioned, and one end of the second oil way (45) is communicated with a first annular groove (81) of the first valve core hole (47); the inner end of the brake release oil path (41) is communicated with the first annular groove (81), and the inner end of the oil return oil path (42) is communicated with the second pilot cavity (47 b).
4. The time delay brake control valve for a hydraulic swing motor according to claim 1, wherein a spring cavity (124) is opened axially inward of an end surface of the throttle valve core (12) away from the pressure measuring valve core, and a second return spring (13) is installed axially in the spring cavity; the side wall of the spring cavity is provided with a slotted hole used for communicating with a first oil way (43); one end of the throttle valve core (12) close to the pressure measuring valve core is provided with a throttle small hole (123), and the inner end of the throttle small hole is communicated with the spring cavity (124).
5. The time delay brake control valve for a hydraulic rotary motor according to claim 4, wherein an end face of the throttle valve core (12) close to the pressure measuring valve core is recessed to form a sinking groove (128), and the throttle orifice is opened on a bottom wall of the sinking groove; the inner diameter of the throttling small hole is smaller than the inner diameter of the bottom of the sinking tank.
6. The time delay brake control valve for a hydraulic rotary motor according to claim 5, characterized in that a third annular groove (129) is further provided in the middle of the throttle valve core in the axial direction, a second throttle valve core hole (125) communicating with the spring cavity is provided in the inner wall of the third annular groove, the side wall of the third annular groove (129) close to the first oil passage is provided as a protruding ring, and a throttle gap (126) is provided between the protruding ring and the inner wall of the second valve core hole (48);
when the throttle valve core is positioned at the first position, the third annular groove (129) is staggered from the first oil duct, and hydraulic oil in the spring cavity flows out of the third annular groove and flows to the first oil duct along the throttle clearance; when the throttle valve core is positioned at the second position, the third annular groove (129) corresponds to the first oil passage, and hydraulic oil in the spring cavity directly flows from the third annular groove (129) to the first oil passage.
7. The time delay brake control valve for a hydraulic rotary motor according to claim 6, wherein a pressure equalizing groove (121) is circumferentially provided in the throttle valve core (12) near a side wall of the sink groove (128), and a first throttle valve core hole (122) is provided in the throttle valve core (12), the pressure equalizing groove being communicated with the sink groove (128) through the first throttle valve core hole (122).
8. The time delay brake control valve for a hydraulic rotary motor according to claim 1, wherein a side wall of one end of the pressure measuring valve core, which is far away from the throttle valve core, is provided with a limit protrusion (96), and the position of the second valve core hole corresponding to the limit protrusion is provided with a limit boss matched with the limit protrusion.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202310107732.XA CN115839357B (en) | 2023-02-10 | 2023-02-10 | Delay brake control valve for hydraulic rotary motor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202310107732.XA CN115839357B (en) | 2023-02-10 | 2023-02-10 | Delay brake control valve for hydraulic rotary motor |
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| CN115839357B true CN115839357B (en) | 2024-01-12 |
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| CN113464356A (en) * | 2021-08-05 | 2021-10-01 | 青岛力克川液压机械有限公司 | Hydraulic driving device suitable for closed system |
| CN217207082U (en) * | 2022-03-18 | 2022-08-16 | 江苏恒立液压科技有限公司 | Control valve and hydraulic motor |
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| NO163892C (en) * | 1971-03-31 | 1990-08-08 | Norwinch A S | HYDRAULIC SYSTEM, PRINCIPLES FOR OPERATING WINDS. |
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| DE1426534B1 (en) * | 1961-03-06 | 1970-08-27 | Moog Inc | Pneumatic or hydraulic adjustment device for a machine support |
| GB1162067A (en) * | 1966-06-23 | 1969-08-20 | Atlas Capco Aktiebolag | Improvements in Means for Unloading and Controlling Compressor Units |
| JP2008104976A (en) * | 2006-10-26 | 2008-05-08 | Furukawa Rock Drill Co Ltd | Hydraulic crusher |
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| CN113464356A (en) * | 2021-08-05 | 2021-10-01 | 青岛力克川液压机械有限公司 | Hydraulic driving device suitable for closed system |
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Address after: 266000 No. 36 Siyuan Road, hi tech Industrial Development Zone, Qingdao, Shandong Patentee after: Qingdao Likechuan Hydraulic Co.,Ltd. Country or region after: China Address before: 266000 No. 36 Siyuan Road, hi tech Industrial Development Zone, Qingdao, Shandong Patentee before: QINGDAO LKC HYDRAULIC Co.,Ltd. Country or region before: China |