CN115839357A - Delay brake control valve for hydraulic rotary motor - Google Patents
Delay brake control valve for hydraulic rotary motor Download PDFInfo
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- CN115839357A CN115839357A CN202310107732.XA CN202310107732A CN115839357A CN 115839357 A CN115839357 A CN 115839357A CN 202310107732 A CN202310107732 A CN 202310107732A CN 115839357 A CN115839357 A CN 115839357A
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- 238000001514 detection method Methods 0.000 claims abstract description 25
- 238000009530 blood pressure measurement Methods 0.000 claims abstract description 8
- 230000000149 penetrating effect Effects 0.000 claims abstract description 4
- 239000003921 oil Substances 0.000 claims description 158
- 230000003111 delayed effect Effects 0.000 claims description 38
- 239000010720 hydraulic oil Substances 0.000 claims description 22
- 238000007789 sealing Methods 0.000 claims description 4
- 230000000994 depressogenic effect Effects 0.000 claims 4
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- 239000007788 liquid Substances 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 238000005299 abrasion Methods 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
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Abstract
The invention discloses a time-delay brake control valve for a hydraulic rotary motor, wherein a valve body of the control valve is horizontally provided with a first valve core hole and a second valve core hole in a penetrating way respectively, and a pilot valve core capable of moving along the axial direction is arranged in the first valve core hole; a throttle valve core and a pressure measuring valve core which can move along the axial direction are arranged in the second valve core hole; the valve body is internally provided with 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; 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; and a pressure detection hole and a pressure detection plug are arranged on the outer wall of the valve body on the side surface of the pressure measurement valve core, and a channel communicated with the second oil path and the pressure detection hole is arranged in the pressure measurement valve core. The time-delay brake control valve is convenient for the pressure intensity detection of the control cavity of the brake controller 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 brake delay in application so as to avoid the problem of transitional wear of a brake pad and a stop ring during emergency braking, and therefore, a delayed brake control valve gradually appears in the market. The existing delay brake control valve mainly has two functions, namely, the function of brake release in a hydraulic rotary motor and the function of brake delay.
However, in practical application, there is a need to detect the pressure in the spring brake control chamber of the rotary motor during braking or brake release, but the structure of the current delayed brake control valve is difficult to meet the requirement, and a pressure detection port for detecting the pressure value of the spring brake control chamber during brake release and delayed brake is lacked.
Therefore, the prior art has yet to be developed.
Disclosure of Invention
In order to solve the technical problems, the invention provides the time-delay brake control valve for the hydraulic rotary motor, and the operability and convenience of pressure detection of the control cavity of the brake controller are realized by improving the internal structure of the valve body and additionally arranging the pressure measuring valve core and the pressure detection port.
In order to solve the above problems, the present invention provides the following technical solutions:
a valve body of the control valve is horizontally provided with a first valve core hole and a second valve core hole in a penetrating way, and a pilot valve core and a first return spring which can move along the axial direction are arranged in the first valve core hole; a second reset spring, a throttle valve core capable of moving along the axial direction and a pressure measuring valve core are sequentially arranged in the second valve core hole; the valve body is internally provided with 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; the outer wall of the valve body is also provided with a normal oil supply way, a pilot oil way, a brake release oil way and an oil return oil way, and the periphery of the pilot valve core is provided with a first annular groove corresponding to the brake release oil way and the normal oil supply way;
a pressure measuring plug is mounted on the pressure measuring hole, and a channel for communicating the second oil path with the pressure measuring hole is formed 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 simultaneously corresponds to the normal oil supply way and the brake release oil way, so that the normal oil supply way is communicated with the brake release oil way;
during braking, the pilot valve element is reset to the second working position, the first annular groove is staggered with the normal oil supply path, the first annular groove only corresponds to the braking release oil path, and the braking release oil path, the first annular groove, the second oil path, the second valve element hole, the first oil path, the second valve element hole and the oil return path are communicated with each other.
Optionally, in the delayed braking control valve, an outer diameter of an inner end of the pressure measuring valve core, which is close to the throttle valve core, is smaller than an inner diameter of the second valve core hole, and an annular gap is formed between an outer periphery of the inner end of the pressure measuring valve core and an inner wall of the second valve core hole.
Optionally, in the delayed brake control valve, a first pressure measuring valve core hole communicated with the second oil path is arranged at the periphery of the pressure measuring valve core, a second pressure measuring valve core hole is arranged on the side wall of the pressure measuring valve core corresponding to the pressure detection 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 located on the inner wall of the second annular groove.
Optionally, in the delayed braking control valve, first plugs are respectively arranged at two ends of a first valve core hole and a second valve core hole, a first return spring is arranged between one end of a pilot valve core and the adjacent first plug, a first pilot cavity is defined between one end of the pilot valve core far away from the first return spring and the adjacent first plug, and a second pilot cavity is defined between the end of the pilot valve core close to the first return spring, the adjacent first plug and the inner wall of the first valve core hole; the first pilot cavity is communicated with the pilot oil way;
the lower end of the first oil way is communicated with the second pilot cavity, the upper end of the first oil way is communicated with the inner side wall of the second valve core hole where the throttling valve core is positioned, and one end of the second oil way is communicated with the first annular groove of the first valve core hole; the inner end of the brake release 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 chamber.
Optionally, in the delayed brake control valve, a spring cavity is axially and inwardly formed in the end face, away from the pressure measuring valve core, of the throttle valve core, and a second return spring is axially installed in the spring cavity; a slotted hole used for communicating the first oil way is formed in the side wall of the spring cavity; one end of the throttling valve core close to the pressure measuring valve core is provided with a throttling small hole, and the inner end of the throttling small hole is communicated with the spring cavity.
Optionally, in the delayed braking control valve, an end face of the throttle valve core, which is close to the pressure measuring valve core, is recessed to form a sink groove, and the throttle small hole is arranged on the bottom wall of the sink groove; the inner diameter of the throttling small hole is smaller than the inner diameter of the bottom of the sink groove.
Optionally, in the delayed brake control valve, a third annular groove is further formed 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, a protruding ring is arranged on the side wall, close to the first oil duct, of the third annular groove, and a throttle gap is formed between the protruding ring and the inner side wall of the second valve core hole.
Preferably, a fourth annular groove is further formed on one side of the protruding ring close to the first oil passage.
When the throttling valve core is located 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 throttling gap, and in the process, the throttling gap achieves a second throttling effect;
when the throttle valve core is located at the second position, the third annular groove corresponds to the first oil duct, and the hydraulic oil in the spring cavity directly flows to the first oil duct from the third annular groove.
Optionally, in the delayed braking control valve, a pressure equalizing groove is circumferentially provided on a side wall of the throttle valve core close to the sinking groove, a first throttle valve core hole is provided 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 throttling valve core, the hydraulic oil can enter the pressure equalizing groove through the first throttling valve core hole, and the phenomenon that the throttling valve core is blocked is prevented.
Optionally, in the delayed brake control valve, one end of the pilot valve core forms a spring mounting post, and one end of the first return spring is sleeved on the spring mounting post.
Optionally, in the delayed braking control valve, a limit protrusion is disposed on a side wall of one end of the pressure measuring valve core, which is far away from the throttle valve core, and a limit boss matched with the limit protrusion is disposed in a position of the second valve core hole, which corresponds to the limit protrusion.
The limiting boss prevents the pressure measuring valve core from approaching to the throttling valve core, and normal operation of the throttling valve core is guaranteed. Preferably, the limit protrusion is a limit head formed by radially expanding the end part of the pressure measuring valve core.
The delay brake 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 intensity detection port, the operability and the convenience of the pressure intensity detection of the control cavity of the brake controller are realized. When the pressure sensor is used, the pressure sensor is connected with the plug at the pressure detection port only after the plug is removed, and then the pressure in the control cavity of the spring brake can be detected when the brake is released or braked by the rotary motor through the connected acquisition instrument.
2. Based on the pressure change of the control cavity of the brake controller, the pressure change of the pressure in the control cavity of the brake collected from the pressure detection port can be further analyzed, the pressure in the control cavity of the brake is multiplied by the contact area of oil to obtain 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 delay time of braking and brake releasing of the delay brake control valve is calculated.
3. The oil circuit of the delayed 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, so that excessive abrasion of a brake pad and a brake ring is avoided, and meanwhile, the pollution of abraded particulate matters of the rubber surface brake pad to the hydraulic oil is reduced.
Drawings
Fig. 1 is a schematic perspective view of an overall structure of a delayed brake control valve according to embodiment 1 of the present invention;
FIG. 2 (1) is a side view of the delayed brake control valve; fig. 2 (2) is a front view of the delayed brake control valve;
FIG. 3 is a sectional view B-B of the delayed brake control valve of FIG. 2 (1) during an operating condition;
FIG. 4 isbase:Sub>A sectional view A-A of the delayed brake control valve of FIG. 3 during an operating condition;
FIG. 5A is a B-B cross-sectional view of the delayed brake control valve in the second operating state; FIG. 5B isbase:Sub>A sectional view A-A of the delayed brake control valve in the second operating state;
FIG. 6 is an enlarged view of the structure of FIG. 3A;
FIG. 7 is a schematic diagram of the pressure sensing spool mechanism;
FIG. 8 is a schematic perspective view, partially in section, of a delayed brake control valve;
wherein the reference numerals are as follows:
1. the rotary motor comprises a rotary motor, 2, a brake assembly, 21, a brake ring, 22, a brake pad, 3, a spring brake, 31, a control cavity, 32, a brake spring, 4, a valve body, 41, a brake release oil path, 42, an oil return oil path, 43, a first oil path, 44, a common oil supply path, 45, a second oil path, 46, a pilot oil path, 47, a first valve core hole, a first pilot cavity 47a, a second pilot cavity 47b, 48, a second valve core hole, 5.O type sealing ring, 6, a first plug, 7, a first return spring, 8, a pilot valve core, 81, a first annular groove, 9, a pressure measuring valve core, 91, a first pressure measuring valve core hole, 92, a second pressure measuring valve core hole, 93, a third pressure measuring valve core hole, 94, an annular gap, 95, a second annular groove, 10, a pressure measuring plug, 11, a double-end screw plug, 12, a valve core, 121, a pressure equalizing groove, 122, a first throttling valve core hole, 123, a throttling small hole, a second throttling small hole, 125, a throttling small hole, a fourth annular groove, 129, a throttling groove and a fourth annular groove; 13. a second return spring, 14, a spring seat.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention. It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may be present. As used in this specification, the terms "vertical," "horizontal," "left," "right," "up," "down," "inner," "outer," "bottom," and the like are used in the orientation or positional relationship indicated in the drawings for convenience in describing the invention and for simplicity in description, and do not indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting. 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. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items. In addition, the technical features involved in the different embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other.
Example 1
As shown in fig. 1 to 5 and 8, the present embodiment provides a delayed brake control valve for a hydraulic swing motor, which is mainly used for brake release and delayed braking of the swing hydraulic motor.
Specifically, as shown in fig. 3 to 5, a first valve core hole 47 and a second valve core hole 48 are respectively horizontally arranged in the valve body 4 of the control valve in a penetrating manner, and a pilot valve core 8 and a first return spring 7 which can reciprocate linearly along the axial direction are arranged in the first valve core hole 47. The second return spring 13, the throttle valve spool 12 that is movable in the axial direction, and the pressure measuring valve spool 9 are sequentially disposed in the second spool hole 48. The two ends of the first valve core hole and the second valve core hole are arranged for plugging. 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 and slidably connected with the pilot valve core. The diameter of the second valve core hole is matched with that of the throttling valve core, and the hole surface of the second valve core hole is attached to the throttling valve core and is in sliding connection with the throttling valve core.
Specifically, the two ends of the first valve core hole and the second valve core hole can be plugged by installing the first plug 6. In this embodiment, the first plug 6 is a G1/4 plug, and is sealed by an O-ring. In other embodiments, the first plug may be fixed to the valve body by a snap-fit method.
One end of the first return spring 7 acts on the pilot valve core, so that the pilot valve core can automatically reset when no hydraulic pressure exists in the valve body, and one end, far away from the first return spring, of the pilot valve core 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 spool 12, so that the throttle valve spool is automatically returned when the second spool bore 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 reason, the first oil circuit and the second oil circuit of this embodiment run through and extend to the valve body outer wall behind the second valve core hole, form the trompil, and this trompil carries out the shutoff through installation double-end plug, keeps the sealed of first oil circuit and second oil circuit.
As shown in fig. 3 to 4, a normal supply oil path 44, a pilot oil path 46, a brake release oil path 41 and an oil return oil path 42 are further formed on the outer wall of the valve body, the pilot oil path 46, the brake release oil path 41 and the normal supply oil path 44 are communicated with the first valve core hole, as shown in fig. 4, the brake release oil path 41 is used for being connected with the control chamber 31 of the spring brake, and a first annular groove 81 corresponding to the brake release oil path 41 and the normal supply oil path 44 is formed in the outer periphery of the pilot valve core.
One end of the pilot valve core 8, which is far away from the first return spring, and the end close to the first plug enclose a first pilot cavity 47a, and a second pilot cavity 47b is enclosed between the end, which is close to the first return spring, of the pilot valve core 8 and the adjacent first plug and between the inner walls of the first valve core holes; the first pilot chamber 47a communicates with the pilot oil passage 46.
The first pilot cavity 47a is a pressure sensing cavity, when the first pilot cavity 47a receives pressure from the pilot oil path, the first pilot valve core is pushed to move linearly 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, the first annular groove 81 corresponds to and is communicated with the normal oil supply path 44 and the brake release oil path 41, so that the normal oil supply path 44 is communicated with the brake release oil path 41, and hydraulic oil introduced into the normal oil supply path can flow into a control cavity of the spring brake through the annular groove and the brake release oil path, so that the spring brake releases the braking state.
When the pressure of the first pilot chamber 47a is released, the pilot spool is reset by the restoring force of the first return spring and returns to the second operating position, the first annular groove 81 is offset from the normal oil supply passage 44, the first annular groove 81 corresponds to only 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 oil return passage 42 are communicated with each other.
On this basis, in order to facilitate the detection of the pressure of the control cavity of the brake controller of the rotary motor, a pressure measuring valve core is arranged in a second valve core hole of the delayed brake control valve, and the pressure measuring valve core and related structures thereof are specifically arranged as follows:
pressure measuring valve core
To facilitate sensing the pressure in the brake controller control chamber of the rotary motor, a pressure sensing spool 48 is disposed in the second spool bore of the delayed brake control valve of the present application. Specifically, as shown in fig. 3 and 7, a pressure detection hole 10a is formed in the outer wall of the valve body on the side surface of the pressure measurement spool 48, a pressure measurement plug 10 is mounted on the pressure detection hole, and a passage communicating the second oil passage 45 and the pressure detection hole is formed in the pressure measurement spool 48. The connection mode of the pressure measuring plug and the pressure intensity detection hole is a detachable connection mode such as screw connection or clamping connection.
Specifically, in this embodiment, the pressure measuring plug 10 is screwed with a pressure detecting hole having a thread therein by using a plug (e.g., ZG1/8 plug). Because the double-end plug and the ZG1/8 plug have the taper thread structures, the taper thread is connected with the thread of the corresponding mounting part of the valve block without arranging a sealing ring, the space is saved, the installation is convenient and fast, and the fixation firmness is higher.
The end of the second valve core hole, which is positioned at the pressure measuring plug, is a pressure measuring end, the outer diameter of the inner end of the pressure measuring valve core 9, which is 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 hydraulic oil from the second oil passage flows along the annular gap toward the throttle valve body 8, flows into the first oil passage through the throttling action of the throttle valve body 8, and flows to the oil return passage along the second pilot chamber 47b of the second valve body bore.
More specifically, a first pressure measuring valve core hole 91 communicated with the second oil path is formed in the periphery of the pressure measuring valve core 9, a second pressure measuring valve core hole 92 is formed in 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 formed in the pressure measuring valve core. In this embodiment, the pressure measuring spool 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 spool hole 91 is located on the inner wall of the second annular groove.
Through the arrangement, the pressure detection hole 10a is communicated with the brake release oil way through the second pressure measuring valve core hole, the third pressure measuring valve core hole, the first pressure measuring valve core hole, the second oil way and the first valve core hole 47, namely, the communication between the pressure detection hole 10a and the control cavity of the spring brake is realized, and therefore, the pressure of the control cavity of the spring brake can be obtained only through the pressure detection in the pressure detection hole 10 a.
When the pressure intensity is detected, the pressure measuring plug on the pressure intensity detecting hole is only needed to be detached, the pressure sensor is connected to the pressure intensity detecting hole in a sealing mode, and the acquisition instrument can detect the pressure intensity in the control cavity of the spring brake when the brake is released or braked by the rotary motor through the pressure sensor; the pressure intensity in the control cavity of the brake is multiplied by the contact area of the oil liquid by the acquisition instrument to obtain 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; specifically, at motor brake delay: calculating and analyzing the time length from the time point when the pressure F1 is equal to F2 to the time point when the pressure F1 is less than F2, namely the time length is the braking delay time; therefore, based on the method, the time for the delayed brake control valve to delay the braking can be deduced by analyzing the collected pressure change in the brake control cavity.
In order to limit the pressure measuring valve core and avoid the situation that the pressure measuring valve core moves to contact with the throttling valve core along the second valve core hole in the working process to hinder the normal work of the throttling valve core, 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 to the throttling valve core, and normal operation of the throttling valve core is guaranteed. 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 brake delay (or throttling effect) of the delayed brake control valve on the rotary motor, the following structure of the delayed brake control valve of the present 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 valve element 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 reset spring 7 acts on the pilot valve core, so that the pilot valve core can automatically reset when no hydraulic pressure exists in the valve body, and the other end of the first reset 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 leading case, avoid increasing extra control oil circuit, simplified the oil circuit.
The lower end of the first oil path is communicated with the second pilot cavity 47b, the upper end of the first oil path is communicated with the inner side wall of the second valve core hole where the throttle valve core is positioned, and one end of the second oil path 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 oil return 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 motion 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 motion distance when the second return spring drives the throttling valve core to return.
Throttle control of throttle valve cartridge
As shown in fig. 3 to 8, a spring cavity 124 is formed in the end surface of the throttle valve core 12 away from the pressure measuring valve core and is opened inward along the axial direction, and a second return spring 13 is axially installed in the spring cavity. In this embodiment, a spring seat 14 is further disposed between the throttle valve core 12 and the adjacent first plug, an outer end of the second return spring is connected to the spring seat, and an inner end of the second return spring is connected to an inner wall of a spring cavity of the throttle valve core. In order to install the second return spring conveniently, the second return spring is in contact with the throttle valve core and the spring seat.
When oil liquid in the second oil path enters the second valve core hole, the throttle 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 oil is not available, the return action of the second return spring drives the throttle valve core to reset. Through setting up second reset spring, realize the automatic re-setting of throttle valve core, avoid increasing extra control oil circuit, simplified the oil circuit.
A slotted hole for communicating the first oil path 43 is formed in the side wall of the spring cavity; 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 a spring cavity 124. Preferably, the end surface of throttle valve core 12 close to the pressure measuring valve core is recessed to form a sink groove 128, and the throttle small hole is arranged on the bottom wall of the sink groove; the inner diameter of the throttling small hole is smaller than the inner diameter of the bottom of the sink groove.
Because the throttle valve core contains the throttle small hole 123, the first throttle can be generated when the hydraulic oil of the control cavity of the brake linkage device flows into the inner cavity of the shell motor, and the brake delay effect is achieved.
On the basis, the middle part of the throttle valve core is also provided with a third annular groove 129 along the circumferential direction, the inner wall of the third annular groove is provided with a second throttle valve core hole 125 communicated with the spring cavity, the side wall of the third annular groove 129 close to the first oil duct is provided with a protruding ring, a throttling gap 126 is arranged between the protruding ring and the inner side 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 projecting ring adjacent to the first oil passage.
When the pressure of the outer end of the throttle valve core is larger than the spring force of the second return spring, the second spring is in a compressed state, and the throttle valve core is located at the first position, the fourth annular groove 127 corresponds to the first oil duct 43, the third annular groove 129 is staggered with the first oil duct 43, the hydraulic oil after the first throttling of the throttling small hole enters the spring cavity, 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 role for the second throttling.
When the pressure of the hydraulic oil received by the pressure sensing end (i.e., 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 under pressure, 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 passage, and the hydraulic oil in the spring cavity directly flows from the third annular groove 129 to the first oil passage. In this state, the valve body realizes one-time throttling only through the small throttling hole.
Further, in order to prevent the throttle valve core from being blocked, the following settings are carried out: the throttle valve core is provided with a pressure equalizing groove 121 along the circumferential direction near the side wall of the sink groove 128, a first throttle valve core hole 122 is arranged in the throttle valve core 12, and the pressure equalizing groove is communicated with the sink groove 128 through the first throttle valve core hole 122. When hydraulic oil passes through the throttling valve core, the hydraulic oil can enter the pressure equalizing groove through the first throttling valve core hole, and the phenomenon that the throttling valve core is blocked is prevented.
Working principle of brake delay and brake release of delayed brake control valve
(1) Braking delay:
as shown in the hydraulic oil flow direction 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 will be reset under the action of the first return spring, and at the same time, the connection between the normal supply oil path 44 and the control chamber 31 of the brake linkage device through the annular groove of the pilot valve core is cut off, at this time, under the action of the brake spring 32, the hydraulic oil in the control chamber 31 of the brake linkage device will slowly return oil to the inner cavity of the motor housing through the brake release oil path 41, the second oil path 45, the annular gap 94, the small throttle hole 123, the spring chamber 124, the second throttle core hole 125, the throttle gap 126, the annular groove 127, the first oil path 43, and the oil return oil path 42, so as to achieve the braking of the rotary motor, and achieve the effect of braking delay through the throttling function, thereby avoiding the excessive wear of the brake pad and the brake ring, and reducing the pollution of the rubber-faced brake pad to the hydraulic oil particles.
(2) And (3) brake release:
as shown in the hydraulic oil flow directions of (1) - (2) - (3) of fig. 5 (a) and (B), when the first pilot cavity 47a receives the pressure from the pilot oil path, the first pilot valve core is pushed to move linearly toward the first return spring, the first return spring is compressed until the pilot valve core moves to the first working position, the first annular groove 81 is communicated with the normal oil path 44 and the brake release oil path 41 at the same time, so that the normal oil path 44 is communicated with the brake release oil path 41, and at this time, the hydraulic oil introduced into the normal oil path can flow into the control cavity of the spring brake through the annular groove and the brake release oil path, so that the spring brake releases the braking state.
The above embodiment 2 is a more optimized structure of the delayed brake control valve, the detailed structure of the delayed brake control valve of the present application is not limited to the embodiment 2, and it will be obvious to those skilled in the art that equivalent substitutions or changes can be made based on the disclosure of the specification, and all such changes or substitutions should fall within the protection scope of the appended claims.
Claims (10)
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 arranged in a valve body (4) in a penetrating manner, and a pilot valve core (8) and a first return spring which can move along the axial direction are arranged in the first valve core hole; a second return spring, a throttle 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); two ends of the first valve core hole and the second valve core hole are arranged in a sealing way, 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; a normal oil supply way (44), a pilot oil way (46), a brake release oil way (41) and an oil return way (42) are further formed in the outer wall of the valve body, and a first annular groove (81) corresponding to the brake release oil way (41) and the normal oil supply way (44) is formed in the periphery of the pilot valve core; a pressure intensity detection hole (10 a) is formed in the outer wall of the valve body on the side face of the pressure measurement valve core (48), a pressure measurement plug (10) is installed on the pressure intensity detection hole, and a channel communicated with the second oil path (45) and the pressure intensity detection hole is formed in the pressure measurement valve core (48);
when the brake is released, the pilot valve core moves to a first working position, and the first annular groove (81) simultaneously corresponds to the normal oil supply way (44) and the brake release oil way (41), so that the normal oil supply way (44) is communicated with the brake release oil way (41);
during braking, the pilot valve core is reset to return to the second working position, the first annular groove is staggered with the normal oil supply path, the first annular groove only corresponds to the braking release oil path (41), and the braking release 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 second valve core hole and the oil return path (42) are communicated with each other.
2. The delayed brake control valve for a hydraulic rotary motor according to claim 1, wherein the outer diameter of the inner end of the pressure measuring spool (9) adjacent to the throttle spool (12) is smaller than the inner diameter of the second spool hole (48), and an annular gap (94) is formed between the outer periphery of the inner end of the pressure measuring spool (9) and the inner wall of the second spool hole.
3. The delayed brake control valve for a hydraulic rotary motor according to claim 2, wherein a first pressure sensing spool hole (91) communicating with the second oil passage is provided at the outer periphery of the pressure sensing spool (9), a second pressure sensing spool hole (92) is provided at the side wall of the pressure sensing spool corresponding to the pressure detection hole (10 a), and a third pressure sensing spool hole (93) communicating the first pressure sensing spool hole (91) and the second pressure sensing spool hole (92) is provided in the pressure sensing spool.
4. The delayed brake control valve for a hydraulic rotary motor according to claim 3, wherein the pressure sensing spool (9) is further provided with a second annular groove (95) corresponding to the outer periphery of the second oil passage, and the first pressure sensing spool hole (91) is located in the inner wall of the second annular groove.
5. The delay brake control valve for the hydraulic rotary motor according to claim 1, wherein the first plug (6) is disposed at each of two ends of the first spool hole and the second spool hole, the first return spring (7) is disposed between one end of the pilot spool (8) and the adjacent first plug, a first pilot cavity (47 a) is defined between one end of the pilot spool (8) far away from the first return spring and the adjacent first plug, and a second pilot cavity (47 b) is defined between one end of the pilot spool (8) close to the first return spring and the inner wall of the adjacent first plug and the first spool hole; the first pilot chamber (47 a) communicates with a pilot oil passage (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).
6. The delayed brake control valve for a hydraulic rotary motor according to claim 1, wherein a spring chamber (124) is opened inward in the axial direction in the end surface of the throttle spool (12) away from the pressure measuring spool, and a second return spring (13) is installed in the spring chamber in the axial direction; a slotted hole used for communicating the first oil way (43) is formed in the side wall of the spring cavity; one end of the throttle valve core (12) close to the pressure measuring valve core is provided with a small throttle hole (123), and the inner end of the small throttle hole is communicated with the spring cavity (124).
7. The delayed brake control valve for a hydraulic swing motor according to claim 6, wherein the end surface of the throttle valve body (12) adjacent to the pressure measuring valve body is recessed to form a depressed groove (128), and the throttle orifice is provided on the bottom wall of the depressed groove; the inner diameter of the throttling small hole is smaller than the inner diameter of the bottom of the sink groove.
8. The delay brake control valve for a hydraulic rotary motor according to claim 7, wherein a third annular groove (129) is further provided in the middle of the throttle valve spool in the axial direction, a second throttle valve spool hole (125) communicating with the spring chamber is provided in an inner wall of the third annular groove, a protruding ring is provided in the third annular groove (129) near a side wall of the first oil passage, and a throttle gap (126) is provided between the protruding ring and an inner side wall of the second valve spool hole (48);
when the throttle valve core is positioned at the first position, the third annular groove (129) is staggered with the first oil duct, and the hydraulic oil in the spring cavity flows out of the third annular groove and flows to the first oil duct along the throttle gap; when the throttle valve core is located at the second position, the third annular groove (129) corresponds to the first oil channel, and hydraulic oil in the spring cavity directly flows to the first oil channel from the third annular groove (129).
9. The delayed brake control valve for a hydraulic rotary motor according to claim 8, wherein the throttle valve body is provided with a pressure equalizing groove (121) along a circumferential direction near a side wall of the depressed groove (128), and a first throttle valve body hole (122) is provided in the throttle valve body (12), and the pressure equalizing groove communicates with the depressed groove (128) through the first throttle valve body hole (122).
10. The delayed brake control valve for a hydraulic swing motor according to claim 3, wherein a stopper protrusion (96) is provided on a side wall of one end of the pressure measuring spool remote from the throttle spool, and a stopper boss which is fitted with the stopper protrusion is provided in the second spool hole at a position corresponding to the stopper protrusion.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310107732.XA CN115839357B (en) | 2023-02-10 | 2023-02-10 | Delay brake control valve for hydraulic rotary motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310107732.XA CN115839357B (en) | 2023-02-10 | 2023-02-10 | Delay brake control valve for hydraulic rotary motor |
Publications (2)
| Publication Number | Publication Date |
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| CN115839357A true CN115839357A (en) | 2023-03-24 |
| CN115839357B CN115839357B (en) | 2024-01-12 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202310107732.XA Active CN115839357B (en) | 2023-02-10 | 2023-02-10 | Delay brake control valve for hydraulic rotary motor |
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| DE1426534B1 (en) * | 1961-03-06 | 1970-08-27 | Moog Inc | Pneumatic or hydraulic adjustment device for a machine support |
| FR2132282B1 (en) * | 1971-03-31 | 1975-06-20 | No | |
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| US20140158469A1 (en) * | 2011-08-04 | 2014-06-12 | Roland Bisig | Control device for a hydraulic drive |
| 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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2023
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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 |
| FR2132282B1 (en) * | 1971-03-31 | 1975-06-20 | No | |
| 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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| CN115839357B (en) | 2024-01-12 |
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