CN211975564U - Duplex reversing valve - Google Patents

Abstract

The utility model discloses a pair switching-over valve, including main part valve, circumference actuating mechanism and axial actuating mechanism. The main body valve is provided with a first valve core and a second valve core, one end of the first valve core is connected to a first servo motor through a first connecting shaft sleeve through a first gear, the other end of the first valve core is abutted against a first linear sliding block, and the first linear sliding block is connected to a first rack; one end of the second valve core is connected with the hand wheel through a second connecting shaft sleeve by a second gear, the other end of the second valve core is abutted against a second linear sliding block, and the second sliding block is connected with a second rack; the first gear is meshed with the second gear, the first rack and the second rack are both meshed with the third gear, and the second servo motor is connected to the third gear. The detection device also comprises a sensor, and detection bar codes are arranged on the connecting shaft sleeve and the linear sliding block. The duplex reversing valve adopts a mode that the valve body is directly matched with the valve core, a valve sleeve structure is omitted, and after the main driving motor is damaged, oil liquid can be continuously reversed through other driving parts, and the position detection of the valve core is realized.

Description

Duplex reversing valve

Technical Field

The utility model belongs to the switching-over valve field, concretely relates to pair switching-over valve.

Background

The fault-tolerant control of the electro-hydraulic reversing technology means that after a part of driving elements are in fault, the hydraulic actuating elements are controlled to continuously complete the reversing function by means of the driving elements which can still normally work. The reversing valve is used as a core element of the electro-hydraulic reversing technology, and the performance and the fault-tolerant control function of the reversing valve directly determine the working performance and the fault-tolerant performance of the electro-hydraulic reversing technology.

At present, an electro-hydraulic reversing valve with a fault-tolerant function does not exist, namely, the electro-hydraulic reversing valve cannot work continuously after a driving part fails. Under the condition of no fault-tolerant function, for some large-scale equipment which is inconvenient to replace the reversing device or occasions which need continuous long-time work, if the driving part of the reversing device breaks down, the work must be stopped, and great loss is caused.

Specifically, the prior art reversing valves have the following disadvantages:

1. the existing electro-hydraulic reversing technology does not have the fault-tolerant characteristic, and for a servo valve, when a driving part which drives a valve core to axially move breaks down, the servo valve cannot continuously work; for the existing rotary valve, when a driving part for controlling the rotation of the valve core breaks down, the rotary valve cannot continuously work, so that the rotary valve cannot meet the use requirements of certain electro-hydraulic reversing systems which are inconvenient to replace driving elements.

2. The existing rotary valve reversing technology generally adopts the design of matching a valve core and a valve sleeve, has a complex structure and higher manufacturing requirement, and therefore, the wide application of the rotary valve reversing technology is limited.

3. The existing rotary valve reversing technology can not effectively realize the detection of the position of the valve core. Under the condition of no valve core position detection method, on one hand, the determination of the zero position of the valve core cannot be realized; on the other hand, in practical application, some situations requiring precise control of the commutation position cannot be satisfied.

SUMMERY OF THE UTILITY MODEL

The to-be-solved technical problem of the utility model is to provide a pair switching-over valve, this pair switching-over valve adopt valve body and the direct complex mode of case, have left out the valve barrel structure, and damage the back at main driving motor (for example, first servo motor, drive valve core circumferential motion), can continue to carry out the fluid switching-over through other drive division (for example, second servo motor, drive valve core axial motion). The real-time detection of the position of the valve core can be realized, and the control precision of the rotary valve is improved.

In order to solve the technical problem, the utility model discloses a following technical scheme:

a duplex reversing valve comprises a main body valve, a circumferential driving mechanism and an axial driving mechanism, wherein one end of the main body valve is connected with the circumferential driving mechanism, and the other end of the main body valve is connected with the axial driving mechanism;

the main body valve is provided with a first valve core and a second valve core, the circumferential driving mechanism comprises a first gear, a second gear, a first connecting shaft sleeve, a second connecting shaft sleeve, a first servo motor and a hand wheel, and the axial driving mechanism comprises a first rack, a second rack, a third gear, a first linear sliding block, a second linear sliding block and a second servo motor;

one end of the first valve core is connected to the first servo motor through the first connecting shaft sleeve through the first gear, the other end of the first valve core abuts against the first linear sliding block, and the first linear sliding block is connected to the first rack; one end of the second valve core is connected to the hand wheel through the second connecting shaft sleeve through the second gear, the other end of the second valve core is abutted against the second linear sliding block, and the second sliding block is connected to the second rack; the first gear is meshed with the second gear, the first rack and the second rack are both meshed with the third gear, and the second servo motor is connected to the third gear; and the number of the first and second groups,

the double-connection reversing valve further comprises a sensor, the first connecting shaft sleeve and the second connecting shaft sleeve are provided with circumferential detection bar codes, the first linear sliding block and the second linear sliding block are provided with axial detection bar codes, and the sensor is matched with the circumferential detection bar codes and the axial detection bar codes to detect the circumferential and axial positions of the first valve core and the second valve core.

In a specific embodiment, the main body valve further comprises a valve body, and the first valve core and the second valve core are arranged in parallel and respectively penetrate through the valve body; the valve body is provided with an oil inlet, an oil outlet, a first working oil port and a second working oil port, and an oil way for communicating the first valve core and the second valve core is arranged inside the valve body.

In a specific embodiment, the oil flows into the valve body from the oil inlet, sequentially flows through the first valve core and the first working oil port, and sequentially flows through the second working oil port and the first valve core during oil return, and flows out of the valve body from the oil outlet; when oil liquid is reversed, the oil liquid flows into the valve body from the oil inlet, sequentially flows through the second valve core and the second working oil port, sequentially flows through the first working oil port and the second valve core during oil return, and flows out of the valve body from the oil outlet.

In an embodiment, the first valve core is provided with a first oil retaining shoulder, a first working shoulder, a second working shoulder and a second oil retaining shoulder in sequence from a first servomotor end to a first rack end.

In a specific embodiment, the first working shoulder and the second working shoulder are both provided with symmetrical throttle ports along the circumferential direction; the first working shoulder and the second working shoulder are both provided with annular grooves facing the first rack, so that the throttle valve port of the first working shoulder is communicated with the first working oil port, and the throttle valve port of the second working shoulder is communicated with the second working oil port.

In a specific embodiment, a third oil retaining shoulder, a third working shoulder, a fourth oil retaining shoulder, a fourth working shoulder, a fifth oil retaining shoulder and a sixth oil retaining shoulder are sequentially arranged on the second valve core from the hand wheel end to the second rack end.

In a specific embodiment, the throttling valve port of the third working shoulder forms a radially penetrating rectangular groove, a first fault-tolerant oil port is arranged on the second valve spool between the third working shoulder and the fourth oil retaining shoulder, a second fault-tolerant oil port is arranged on the second valve spool between the fifth oil retaining shoulder and the sixth oil retaining shoulder, an oil path communicating the throttling valve port of the third working shoulder, the first fault-tolerant oil port and the second fault-tolerant oil port is arranged inside the second valve spool, and the second fault-tolerant oil port is communicated with the second working oil port through the oil path of the valve body.

In a specific embodiment, the third working shoulder is circumferentially provided with symmetrical throttle ports; the third working shoulder is provided with an annular groove facing the hand wheel, and the bottom of the annular groove is provided with a through hole.

In a specific embodiment, one end of the first valve core and one end of the second valve core are respectively sleeved with a return spring.

In a specific embodiment, the oil inlet and the oil outlet respectively penetrate through the valve body to form through holes.

Adopt the utility model discloses following beneficial effect has:

1. duplex switching-over valve, not only can realize the fluid switching-over, can also use another servo motor control case axial motion to continue to realize the fluid switching-over after the rotatory servo motor of control case breaks down, can satisfy the requirement of some inconvenient dismouting occasion to reversing arrangement fault-tolerance ability.

2. Duplex switching-over valve, adopt the direct and case matched with mode of valve body for its commentaries on classics valve structure has obtained the simplification, has still reduced the number of parts that need to process, has reduced manufacturing cost.

3. Duplex switching-over valve, compare with current rotary valve, adopted initial zero-bit design, effectively avoided relevant problems such as hydraulic actuator mistake start-up that causes because of the starting position is unclear.

4. The pair reversing valve, cooperate through adopting rack and pinion drive mechanism and answer spring, can realize case axial position's control more conveniently. In addition, through a gear rack mechanism, the two valve cores can move in opposite directions, and the fault-tolerant function can be realized more conveniently.

5. Duplex switching-over valve, through arranging the detection bar code on connecting sleeve and sharp slider, can realize the real-time detection of case position, improved the control accuracy of this change valve.

Drawings

Fig. 1 is a schematic structural diagram of a duplex reversing valve according to an embodiment of the present invention;

FIG. 2 is a cross-sectional view of the valve body;

FIG. 3 is a perspective view of the first valve cartridge and an exploded view thereof;

FIG. 4 is a schematic structural view of a first valve spool;

FIG. 5 is a schematic diagram of a second valve spool;

FIG. 6 is a schematic view of an axial initial operating position of the valve spool;

FIG. 7 is a schematic view of a circumferential initial operating position of the valve spool;

FIG. 8 is a cross-sectional view of the body valve;

FIG. 9 is a perspective view of the connecting bushing;

FIG. 10 is a perspective view of a linear slide;

FIG. 11 is a schematic view of the double-link reversing valve in a normal operating position I;

FIG. 12 is a schematic view of the double link diverter valve in the normal operating position II;

FIG. 13 is a schematic view of the double link diverter valve in a fault tolerant operating position I;

fig. 14 is a schematic view of the double link diverter valve in the fault tolerant operating position II.

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, not all, of the embodiments of the present invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.

Referring to fig. 1-14, the utility model discloses a pair switching-over valve, including circumference actuating mechanism, main part valve (including valve body 3 and valve core part), axial actuating mechanism. The circumferential driving mechanism comprises a first servo motor 11, a gear transmission mechanism 12 (in one embodiment, a first gear, a fourth gear and a second gear which are meshed in sequence are included, in another embodiment, a first gear and a second gear which are meshed with each other are included), a connecting shaft sleeve (comprising a first connecting shaft sleeve and a second connecting shaft sleeve) and a hand wheel 13; the valve core part comprises a first valve core 21 and a second valve core 22; the axial driving mechanism comprises a second servo motor 42, a third gear 41, a rack 43 (comprising a first rack and a second rack) and a linear slider (comprising a first linear slider and a second linear slider). The first servo motor 11 can drive the two valve cores to synchronously rotate through the gear transmission mechanism 12, and the hand wheel 13 can manually adjust the circumferential positions of the valve cores; the second servo motor 42 can drive the third gear 41 to rotate, so as to drive the two racks to move linearly, and further to cause the two valve cores to move axially. Since both racks are engaged with the third gear 41, when the third gear rotates, both racks will move in opposite directions, and thus both spools move in opposite directions under the driving of the servo motor 42.

The valve body 3 includes a valve core mounting groove 31, an oil inlet 32, an oil outlet 33, two working oil ports 34, 35, a bolt connecting hole 36, an oil through groove 37 (i.e. an oil path which is arranged inside the valve body 3 and communicates the first valve core and the second valve core) and an oil groove plug 38 which is matched with the oil through groove. Wherein, the oil inlet 32 (or called as P port), the oil outlet 33 (or called as T port) are respectively communicated with the pump station and the oil tank through pipelines; the two working oil ports 34 (ports A) and 35 (ports B) are respectively communicated with the hydraulic actuating element through internal channels; in one embodiment, the diameter D1 of the oil passing groove 37 is 6 mm.

Taking the connection structure of the first valve core 21 as an example (the second valve core adopts a similar connection structure), the first valve core 21 is assembled with a connection shaft sleeve 22 (i.e. a first connection shaft sleeve), a valve core retainer ring 23, spring sleeves 24 and 26, a return spring 25, a thrust bearing 27, a steel ball 28 and a linear slide block 29. The embodiment of the utility model provides an in, first case, second case all with the direct cooperation of valve body to realize switching on and closing of corresponding oil circuit. The first valve core is connected with the first gear and the first servo motor 11 through the connecting shaft sleeve 22 (or further through a coupler), so that the torque of the first servo motor can be transmitted to the first valve core, and the first valve core is driven to rotate; the first valve core abuts against the linear sliding block 29 (namely, the first linear sliding block) (or the first valve core is in rotational connection with the first linear sliding block), the linear sliding block 29 is connected with a first rack through threaded connection, and the first rack makes linear reciprocating motion to drive the first valve core to make axial motion; the return spring 25 may be used for returning the axially displaced position of the first spool and also for preventing hydrodynamic disturbances to ensure stability during operation of the valve.

The first valve spool is provided with a coupling key groove 211, a first oil retaining land 212a, a second oil retaining land 212b, a first land 213a, and a second land 213 b. Wherein, the working shoulder is provided with a throttle valve port through which oil can flow; the oil blocking shoulder can block the oil flow.

The second valve core is provided with a connecting key groove 221, a third working shoulder 223a, a fourth working shoulder 223b, a third gear oil shoulder 222a, a fourth gear oil shoulder 222b, a fifth gear oil shoulder 222c, a sixth gear oil shoulder 222d, a first fault-tolerant oil port 224a and a second fault-tolerant oil port 227. Wherein, the working shoulder is provided with a throttle valve port through which oil can flow; the interior of the second valve core is of a hollow structure, so that oil can flow through the interior of the second valve core from the throttle valve port of the third working shoulder 223a and flow to the first fault-tolerant oil port 224a and the second fault-tolerant oil port 227; each oil blocking shoulder can block the oil flow. The fault-tolerant oil port 224a is formed in the right side of the third working shoulder 223a, the second fault-tolerant oil port 227 is formed in the right side of the fourth working shoulder 223b, and the bottom of the annular groove of the fourth working shoulder 223b is provided with a through hole 224 b. The two fault-tolerant oil ports can continuously realize the conduction or the closing of the corresponding oil circuit after the first servo motor 11 breaks down.

In a specific embodiment, the matching structure of the working shoulder and the oil through groove of the valve core is as shown in fig. 6, the diameter D1 of the oil through groove on the designed valve body is 6mm, and the structural dimensions of all the working shoulders designed by the valve core satisfy the following relationship L1-L3-L2-6 mm. According to the matched structural parameters and the valve core structure, when the opening part of the working shoulder of the valve core (namely, a throttle valve port) and the oil through groove of the valve body are at the same axial position (as shown in a working state in figure 6 a), the oil circuit can be switched on and off alternately in the rotating process of the valve core; when the opening part of the working shoulder of the valve core (namely the throttle valve port) and the oil through groove of the valve body do not overlap in the axial direction (as shown in the working states b and c in fig. 6), the oil path is kept in a closed state all the time during the rotation of the valve core. In addition, because the two valve cores are driven by the two racks to linearly move in opposite directions, when the L1 part of the first valve core is partially overlapped with the oil through groove D1 (i.e., as shown in the working state b in fig. 6), the L3 part of the second valve core is fully overlapped with the D1 part of the oil through groove (i.e., as shown in the working state c in fig. 6), and at this time, the oil passages corresponding to the two valve cores are both in a closed state, which can be used as the axial initial working position of the valve cores.

Similarly, when the valve element rotates in the circumferential direction, the initial position of the circumferential rotation of the first valve element can be determined according to the relative position relationship between the opening portion of the valve element land and the oil through groove of the valve body, as shown in fig. 7.

In the initial operating state, in order to prevent the problem of the false start of the hydraulic actuator caused by the position problem of the spool, the initial operating position of the spool is determined according to the axial and circumferential zero positions of the spool as shown in fig. 8. Before starting oil supply and after finishing oil supply, the first servo motor 11 and the second servo motor 41 drive the valve core to move to the position shown in fig. 8 according to the detection result of the valve core position. At the moment, the opening part of the working shoulder of the valve core is not overlapped with the oil through groove of the valve body along the axial direction and the circumferential direction, the working shoulder of the valve core cuts off the oil way, the oil inlet P and the oil return port T are not directly communicated with the cavity of the hydraulic actuating element, the problems of mistaken starting of the hydraulic actuating element and the like can be effectively avoided, and the hydraulic actuating element is protected.

In one embodiment, the connecting sleeve 22 and the linear slider 29 are respectively disposed with a detecting bar code for detecting the position of a sensor (e.g. a photoelectric sensor), as shown in fig. 9 and 10. The connecting shaft sleeve is circumferentially provided with detection bar codes (called circumferential detection bar codes) with different widths, and the circumferential position detection of the valve core can be realized by matching with a sensor; the linear sliding block is provided with detection bar codes (called axial detection bar codes) with different widths along the axial direction, and the axial position detection of the valve core can be realized by matching with a sensor. The real-time detection of the position of the valve core can be realized through the two groups of detection bar codes.

Under the normal working condition of the duplex reversing valve (i.e. when the first servo motor is not in fault), when the valve core is in the normal working position I as shown in fig. 11, oil flows from the oil inlet P to the first working oil port a through the first working shoulder of the first valve core during oil inlet, and flows from the second working oil port B to the oil return port T through the second working shoulder of the first valve core during oil return; when the valve core is in another normal working position II as shown in fig. 12, the oil flows from the oil inlet P to the second working oil port B through the third working shoulder of the second valve core and the second fault-tolerant oil port, and during oil return, the oil flows from the first working oil port a to the oil return port T through the fourth working shoulder of the second valve core. Therefore, the first servo motor 11 drives the valve core to rotate, and oil liquid reversing can be achieved. In addition, by controlling the axial and circumferential positions of the valve core, the overlapping area of the opening part (namely a throttle valve port) of the working shoulder of the valve body and the oil through groove can be realized, and the flow rate of oil flowing through the valve core can be further adjusted.

Under normal operating conditions, the first servo motor 11 needs to perform continuous rotation operation, and the second servo motor 41 does not operate, so that the first servo motor 11 has a longer operating time and is more prone to malfunction than the second servo motor 41. When the first servo motor 11 fails and cannot rotate, the second servo motor 41 can drive the two valve cores to do linear reciprocating movement, and the corresponding oil passages are continuously switched on and off. When the first valve core is in the closed position, the two valve cores can axially move to the fault-tolerant working position I shown in fig. 13, at the moment, oil flows to the first working oil port A from the oil inlet P through the first valve core, and during oil return, the oil flows to the oil return port T from the second working oil port B through the first valve core, so that the oil circuit with the same function as the normal working position I is conducted; when the second valve core is in the closed position, the two valve cores can axially move to the fault-tolerant working position II as shown in fig. 14, at this time, the oil flows from the oil inlet P to the second working oil port B through the first fault-tolerant oil port and the second fault-tolerant oil port of the second valve core, and during oil return, the oil flows from the first working oil port a to the oil return port T through the second valve core, so that the oil circuit with the same function as the normal working position II is conducted. Therefore, in the case of a failure of the first servo motor 11, the second servo motor 41 is relied upon to achieve the conduction and the closing of the corresponding oil passage.

Because the circumferential position of the valve core is not clear when the first servo motor 11 fails, the two valve cores can be divided into three cases according to the positions of the two valve cores when the first servo motor 11 fails.

(1) If the first servo motor 11 fails, the first valve core is in the open position, and the second valve core is in the closed position, at this time, the second servo motor 41 drives the two valve cores to move between the normal working position I and the fault-tolerant working position II, and oil reversing can be achieved.

(2) If the first servo motor 11 fails, the second valve core is in the open position, and the first valve core is in the closed position, at this time, the second servo motor 41 drives the two valve cores to move between the normal working position II and the fault-tolerant working position I, and oil reversing can be achieved.

(3) If the first servo motor 11 fails, the two valve cores are both in the closed position, and at this time, the second servo motor 41 drives the two valve cores to move between the fault-tolerant working position I and the fault-tolerant working position II, so that oil reversing can be realized.

In addition, when fault-tolerant control is realized, the area of an oil passage can be adjusted by controlling the axial position of the valve core, and the flow of oil flowing through the valve core is further adjusted.

It is to be understood that the exemplary embodiments described herein are illustrative and not restrictive. While one or more embodiments of the present invention have been illustrated in the accompanying drawings, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims.

Claims (10)

1. A duplex reversing valve is characterized by comprising a main body valve, a circumferential driving mechanism and an axial driving mechanism, wherein one end of the main body valve is connected with the circumferential driving mechanism, and the other end of the main body valve is connected with the axial driving mechanism;

the main body valve is provided with a first valve core and a second valve core, the circumferential driving mechanism comprises a first gear, a second gear, a first connecting shaft sleeve, a second connecting shaft sleeve, a first servo motor and a hand wheel, and the axial driving mechanism comprises a first rack, a second rack, a third gear, a first linear sliding block, a second linear sliding block and a second servo motor;

one end of the first valve core is connected to the first servo motor through the first connecting shaft sleeve through the first gear, the other end of the first valve core abuts against the first linear sliding block, and the first linear sliding block is connected to the first rack; one end of the second valve core is connected to the hand wheel through the second connecting shaft sleeve through the second gear, the other end of the second valve core is abutted against the second linear sliding block, and the second linear sliding block is connected to the second rack; the first gear is meshed with the second gear, the first rack and the second rack are both meshed with the third gear, and the second servo motor is connected to the third gear; and the number of the first and second groups,

the double-connection reversing valve further comprises a sensor, the first connecting shaft sleeve and the second connecting shaft sleeve are provided with circumferential detection bar codes, the first linear sliding block and the second linear sliding block are provided with axial detection bar codes, and the sensor is matched with the circumferential detection bar codes and the axial detection bar codes to detect the circumferential and axial positions of the first valve core and the second valve core.

2. The double reversing valve of claim 1, wherein the main body valve further comprises a valve body, and the first valve spool and the second valve spool are arranged in parallel and respectively penetrate through the valve body; the valve body is provided with an oil inlet, an oil outlet, a first working oil port and a second working oil port, and an oil way for communicating the first valve core and the second valve core is arranged inside the valve body.

3. The double reversing valve according to claim 2, wherein oil flows into the valve body from the oil inlet, sequentially flows through the first valve core and the first working oil port, sequentially flows through the second working oil port and the first valve core during oil return, and flows out of the valve body from the oil outlet; when oil liquid is reversed, the oil liquid flows into the valve body from the oil inlet, sequentially flows through the second valve core and the second working oil port, sequentially flows through the first working oil port and the second valve core during oil return, and flows out of the valve body from the oil outlet.

4. The double directional valve as recited in claim 3 wherein the first spool has a first oil retaining land, a first working land, a second working land, and a second oil retaining land disposed in sequence from the first servomotor end to the first rack end.

5. The double reversing valve as defined in claim 4, wherein the first and second work shoulders are each circumferentially provided with symmetrical throttle ports; the first working shoulder and the second working shoulder are both provided with annular grooves facing the first rack, so that the throttle valve port of the first working shoulder is communicated with the first working oil port, and the throttle valve port of the second working shoulder is communicated with the second working oil port.

6. The double reversing valve according to any one of claims 3 to 5, wherein a third oil retaining shoulder, a third working shoulder, a fourth oil retaining shoulder, a fourth working shoulder, a fifth oil retaining shoulder and a sixth oil retaining shoulder are sequentially arranged on the second valve core from the hand wheel end to the second rack end.

7. The tandem reversing valve according to claim 6, wherein the throttling valve port of the third working shoulder forms a rectangular groove penetrating in the radial direction, a first fault-tolerant oil port is arranged on the second valve spool between the third working shoulder and the fourth oil retaining shoulder, a second fault-tolerant oil port is arranged on the second valve spool between the fifth oil retaining shoulder and the sixth oil retaining shoulder, an oil path communicating the throttling valve port of the third working shoulder, the first fault-tolerant oil port and the second fault-tolerant oil port is arranged inside the second valve spool, and the second fault-tolerant oil port is communicated with the second working oil port through the oil path of the valve body.

8. The double reversing valve as defined in claim 7, wherein the third working shoulder is circumferentially provided with symmetrical throttle ports; the third working shoulder is provided with an annular groove facing the hand wheel, and the bottom of the annular groove is provided with a through hole.

9. The double reversing valve according to claim 1, wherein one end of each of the first valve spool and the second valve spool is sleeved with a return spring.

10. The double reversing valve as claimed in claim 2, wherein the oil inlet and the oil outlet each form a through hole through the valve body.

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