CN221074483U - Engineering machinery hydraulic rotary motor and engineering machinery - Google Patents
Engineering machinery hydraulic rotary motor and engineering machinery Download PDFInfo
- Publication number
- CN221074483U CN221074483U CN202322997905.8U CN202322997905U CN221074483U CN 221074483 U CN221074483 U CN 221074483U CN 202322997905 U CN202322997905 U CN 202322997905U CN 221074483 U CN221074483 U CN 221074483U
- Authority
- CN
- China
- Prior art keywords
- oil
- valve
- hydraulic control
- communicated
- hydraulic
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000000605 extraction Methods 0.000 claims abstract description 45
- 238000011084 recovery Methods 0.000 claims abstract description 21
- 230000001502 supplementing effect Effects 0.000 claims description 37
- 238000010276 construction Methods 0.000 claims description 8
- 239000012530 fluid Substances 0.000 claims 4
- 239000003921 oil Substances 0.000 description 150
- 230000002265 prevention Effects 0.000 description 11
- 230000009471 action Effects 0.000 description 7
- 239000010720 hydraulic oil Substances 0.000 description 5
- 230000003139 buffering effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000005265 energy consumption Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000001133 acceleration Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 230000000151 anti-reflux effect Effects 0.000 description 1
- 230000001174 ascending effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 230000007123 defense Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000002427 irreversible effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
Landscapes
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Abstract
The utility model discloses a hydraulic rotary motor of engineering machinery and engineering machinery, wherein the motor is provided with a first cavity and a second cavity, a main oil port A is communicated with the first cavity through a first main oil way, a main oil port B is communicated with the second cavity through a second main oil way, an energy recovery module is arranged between the first main oil way and the second main oil way, the energy recovery module comprises a hydraulic control proportional valve (2.3) and a flow extraction switch valve (2.2), the hydraulic control proportional valve is provided with a first hydraulic control end, a second hydraulic control end, an oil inlet and an oil outlet, the first hydraulic control end is communicated with an inlet end of the energy recovery module, the second hydraulic control end is communicated with the inlet end through a throttling orifice, the oil inlet is communicated with the inlet end, the oil outlet is communicated with a flow release oil port P, meanwhile, the throttling orifice and the second hydraulic control end are communicated with an inlet of a flow extraction switch valve, and an outlet of the flow extraction switch valve is communicated with a compensation oil port M. The utility model can prevent overflow when the rotation is started by the energy recovery module and recover energy when the rotation is braked.
Description
Technical Field
The utility model relates to a hydraulic rotary motor of engineering machinery and the engineering machinery.
Background
The engineering machinery is widely used in industries such as buildings, bridges, high-speed rails, tunnels, wharfs, military industry and the like, and plays a role of a middle-flow column in national capital construction, house construction and national defense construction. Most engineering machinery operations can involve the rotation of a loading platform around a rotation support, and are mostly realized by a hydraulic rotation motor. A schematic diagram of a conventional swing motor hydraulic system is shown in fig. 1.
The conventional rotary motor hydraulic system mainly comprises the following circuits:
1) Rotary buffer loop
When the engineering machinery rotates in full load, the moment of inertia of the boarding vehicle is large, and when the braking or the sudden reversing is started, great impact is caused on a hydraulic system, vibration and noise are generated, and even hydraulic elements are damaged. Therefore, the rotary motor is provided with a plurality of buffer loops, and hydraulic elements such as the buffer overflow valve 1.2 are utilized to ensure that the oil in the high-pressure cavity of the rotary motor is discharged when the oil exceeds a certain pressure, thereby achieving the effect of buffering the oil way.
2) Rebound prevention loop
When the rotary motor is braked, the rotary motor continuously rotates for a certain angle in the original movement direction under the action of inertia, and the oil pressure of one cavity can be increased due to the compression of the volume of the cavity, so that the rotary motor generates a counter-rotation trend, namely rebound. Therefore, the rotary motor is provided with the rebound prevention valve 1.1, the hydraulic oil in two cavities of the rotary motor is connected through the throttle of the middle chamber of the rebound prevention valve, the hydraulic oil in the high-pressure cavity can rapidly flow to the low-pressure cavity through the throttle during braking, and the pressures in the two cavities are dynamically balanced to prevent rebound.
3) Oil supplementing loop
When the rotary motor is braked, the rotary motor can continuously rotate for a certain angle in the original movement direction under the action of inertia, the oil pressure of one cavity can be reduced due to the increase of the volume of the cavity, and even the tendency of idle running and negative pressure formation is caused, so that the service life of the element is influenced. Therefore, the rotary motor is provided with a plurality of oil supplementing loops, the two cavities are connected with the total oil return path through the oil supplementing one-way valve 1.3, the total oil return path is provided with a certain back pressure, and oil can be quickly supplemented under the back pressure effect when the pressure of the cavity is low.
However, the conventional swing motor hydraulic system has the following problems:
1) When the rotary motor is started, the rotating speed is low, the required flow is low, the output flow of the hydraulic pump part overflows through the buffer overflow valve 1.2, and the hydraulic energy is finally lost in a thermal mode.
2) During rotary braking, the kinetic energy is large during rotary platform braking due to the fact that the mass, the rotational inertia and the moment of inertia of the rotary platform and the working device are large, and the kinetic energy is generally lost in the form of heat energy.
3) Most of energy of rotary starting overflow and rotary braking is wasted through heating, the temperature of hydraulic oil is increased rapidly, a special cooling device is needed for cooling, and system power consumption is further increased.
4) The driving moment is limited by the set pressure of the buffer type overflow valve 1.2, the set pressure of the buffer type overflow valve 1.2 is determined by the braking moment of the boarding platform, the driving moment can be insufficient when the loading platform rotates at a slope or is fully loaded, the rated pressure of an actual system is about 34Mpa, and the peak allowable pressure is higher, so that the driving moment of the rotary motor has a large lifting space.
With the development of industry and the increase of market conservation quantity, the accumulated fuel consumption of engineering machinery is rapidly increased, and the engineering machinery becomes a main petrochemical energy consumption body following an automobile. The current petrochemical energy reserves are increasingly reduced and are not renewable in a short time, and the unit price is continuously increased, so that the energy consumption condition becomes an important index for evaluating the market competitiveness of the excavator. High efficiency, energy conservation and emission reduction become irreversible development trend of the hydraulic excavator.
Disclosure of utility model
The utility model aims to solve the technical problems that the existing engineering machinery hydraulic rotary hydraulic system is limited in limit working condition driving moment such as overflow during rotary starting and energy waste during rotary braking through heating, slope rotary full-load rotary and the like.
In order to solve the technical problems, the utility model adopts the following technical scheme:
The hydraulic rotary motor of the engineering machinery comprises a motor body, wherein a main oil port A, a main oil port B and an oil supplementing port M are arranged on the motor body, a motor is arranged in the motor body, the motor is provided with a first cavity and a second cavity, the main oil port A is communicated with the first cavity through a first main oil way, the main oil port B is communicated with the second cavity through a second main oil way, an energy recovery module is arranged between the first main oil way and the second main oil way, a flow release oil port P is arranged on the motor body, the energy recovery module comprises an inlet end, an outlet end, a hydraulic control proportional valve, a flow extraction switch valve and a throttle opening, the inlet end is communicated with the first main oil way and the second main oil way, the outlet end is communicated with the flow release oil port P, the hydraulic control proportional valve is provided with a first hydraulic control end, a second hydraulic control end, an oil inlet and an oil outlet, the first hydraulic control end is communicated with the inlet end, the second hydraulic control end is communicated with the inlet end through the throttle opening, the inlet end is communicated with the inlet end, the flow extraction switch valve is simultaneously communicated with the inlet end and the flow supplementing valve, and the flow valve is closed when the flow is in the flow proportional valve is closed; when the pressure of the oil inlet of the hydraulic control proportional valve is larger than the opening pressure of the flow extraction switching valve, the flow extraction switching valve is opened, the opening degree of the hydraulic control proportional valve is increased along with the increase of the pressure difference between the oil inlet of the hydraulic control proportional valve and the opening pressure of the flow extraction switching valve, and is reduced along with the decrease of the pressure difference between the oil inlet of the hydraulic control proportional valve and the opening pressure of the flow extraction switching valve.
According to the utility model, the energy recovery module is connected between the first main oil way and the second main oil way of the rotary motor, when the system pressure of the rotary motor is larger than the opening pressure of the flow extraction switching valve, the flow extraction switching valve is opened, meanwhile, the opening degree of the hydraulic control proportional valve is increased along with the increase of the oil inlet pressure of the hydraulic control proportional valve and the opening pressure difference of the flow extraction switching valve, and is reduced along with the decrease of the oil inlet pressure of the hydraulic control proportional valve and the opening pressure difference of the flow extraction switching valve, so that when the system is started and braked in a rotary way, obvious pressure difference occurs at two sides of a throttle opening, and meanwhile, the first hydraulic control end and the second hydraulic control end of the hydraulic control proportional valve are obviously different, so that the opening degree of the hydraulic control proportional valve is increased, and further, the hydraulic energy can be recovered through the hydraulic control proportional valve and the flow release oil port P, thereby not only preventing overflow during rotary starting, but also recovering kinetic energy generated during rotary braking and reducing system power consumption; when the rotation is accelerated and the rotation is approximately uniform, the pressure difference at the two sides of the throttle opening is smaller, the opening degree of the hydraulic control proportional valve is small, and the hydraulic energy of the system is basically used for supplying the operation of the rotation motor without influencing the normal operation of the rotation motor.
Preferably, the energy recovery module further comprises an anti-reflux one-way valve mounted at the inlet end of the energy recovery module.
Preferably, the energy recovery module further comprises a safety valve mounted at the outlet end of the energy recovery module.
Preferably, the orifice is replaced by a throttle valve.
Preferably, an oil supplementing one-way valve is installed between the first main oil way and the second main oil way, an inlet of the oil supplementing one-way valve is communicated with the oil supplementing port M, and an outlet of the oil supplementing one-way valve is communicated with the first cavity and/or the second cavity of the motor.
Preferably, the motor body is further provided with an oil drain port Dr, and the inner end of the oil drain port Dr is communicated with the motor.
Based on the same inventive concept, the utility model also provides engineering machinery, which comprises the hydraulic rotary motor of the engineering machinery.
Compared with the prior art, the utility model has the beneficial effects that:
(1) The utility model not only has the conventional functions of the conventional rotary motor: 1) Buffering; 2) Rebound prevention; 3) The low-pressure cavity is filled with oil to prevent idling; 4) The system pressure is cut off (protected) when the system pressure exceeds the limit, and the system also has a new function which is not possessed by the conventional rotary motor: 1) Starting an anti-overflow; 2) Braking energy recovery; 3) The maximum working torque is controllable (temporary supercharging), so that waste caused by the fact that the output flow of a hydraulic pump (main pump) part overflows through a rotary motor overflow valve and finally hydraulic energy is converted into heat energy to escape is avoided, and meanwhile, the utility model avoids the loss of huge kinetic energy generated during rotary braking in a heat energy mode.
Drawings
In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are some embodiments of the present utility model, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
Fig. 1 is a hydraulic schematic diagram of a conventional swing motor.
Fig. 2 is a hydraulic schematic diagram of the hydraulic swing motor of the construction machine according to the present utility model.
In the figure:
1.1-rebound prevention valve; 1.2-buffer overflow valve; 1.3-an oil supplementing one-way valve; 1.4-motor; a is a main oil port; b-a main oil port; m-an oil supplementing port; dr-an oil drain port;
2.1-a safety valve; 2.2-flow extraction on-off valve; 2.3-a hydraulically controlled proportional valve; 2.4-restriction; 2.5-a reverse flow prevention check valve; 2.6-oil supplementing one-way valve; 2.7-motor; p-flow relief port.
Detailed Description
The utility model is further described below in connection with specific preferred embodiments, but it is not intended to limit the scope of the utility model.
In the description of the present utility model, it should be noted that the positional or positional relationship indicated by the terms "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the positional or positional relationship shown in the drawings, are merely for convenience of describing the present utility model and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present utility model. Furthermore, the terms "first," "second," "third," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present utility model, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; may be a mechanical connection; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present utility model will be understood in specific cases by those of ordinary skill in the art.
Referring to fig. 2, an embodiment of the multifunctional hydraulic rotary motor for engineering machinery of the present utility model includes a motor body 2, a main oil port a, a main oil port B, a flow release oil port P, an oil drain port Dr, and an oil supplementing port M for externally connecting an oil path are disposed on the motor body 2, and a safety valve 2.1, a flow extraction switch valve 2.2, a pilot operated proportional valve 2.3, a throttle orifice 2.4, a backflow prevention check valve 2.5, an oil supplementing check valve 2.6, and a motor 2.7 are disposed in the motor body 2.
The hydraulic rotary motor is a new function added on a conventional hydraulic rotary motor, wherein a main oil port A, a main oil port B, an oil drain port Dr and an oil supplementing port M are all of the existing structure, and a safety valve 2.1, a flow extraction switch valve 2.2, a hydraulic control proportional valve 2.3, a throttle port 2.4, an anti-backflow one-way valve 2.5, an oil supplementing one-way valve 2.6 and a motor 2.7 are all of the existing equipment.
The main port A, B is connected to an oil source of a host machine (i.e., a construction machine). The flow release oil port P is a pressure oil release oil port and is connected with an energy storage element or an execution element of the carrying host. The oil drain port Dr is used for discharging the oil body in the motor body casing, and the oil drain port Dr is connected with the loading host computer oil tank. The oil supplementing port M is connected with an oil return path of the carrying host machine, and a certain back pressure is required to be set between the oil return path and the oil tank of the carrying host machine.
The motor 2.7 is provided with a first cavity and a second cavity, the main oil port A is communicated with the first cavity through a first main oil way, the main oil port B is communicated with the second cavity through a second main oil way, and an energy recovery module is arranged between the first main oil way and the second main oil way.
The energy recovery module comprises an inlet end, an outlet end, a hydraulic control proportional valve 2.3, a flow extraction switch valve 2.2 and a throttle opening 2.4, wherein the inlet end is communicated with a first main oil way and a second main oil way through an anti-backflow one-way valve 2.5, the outlet end is communicated with a flow release oil port P, the hydraulic control proportional valve 2.3 is provided with a first hydraulic control end, a second hydraulic control end, an oil inlet and an oil outlet, the first hydraulic control end is communicated with the inlet end, the second hydraulic control end is communicated with the inlet end through the throttle opening 2.4, the oil inlet is communicated with the inlet end, the oil outlet is communicated with a flow release oil port P through the outlet end, meanwhile, the throttle opening 2.4 and the second hydraulic control end are communicated with an inlet of the flow extraction switch valve 2.2, and an outlet of the flow extraction switch valve 2.2 is communicated with an oil supplementing port M.
The oil outlet of the hydraulic control proportional valve 2.3 is provided with a safety valve 2.1, the outlet of the safety valve 2.1 is connected with the oil supplementing port M, namely, a low-pressure oil way is arranged between the outlet of the flow extraction switch valve 2.2 and the outlet of the safety valve 2.1 and the oil supplementing port M, hydraulic oil can flow from the flow extraction switch valve 2.3 and the safety valve 2.1 to the oil supplementing port M, and the motor 2.7 is supplemented with oil through the oil supplementing port M and the oil supplementing one-way valve 2.6 or is connected with an oil return way of a carrying host machine through the oil supplementing port M.
As described above, the rotary motor of the present utility model is provided with the flow extraction oil passage: the first cavity and the second cavity of the motor 2.7 are connected with the inlet of the backflow prevention one-way valve 2.5, the outlet of the backflow prevention one-way valve 2.5 is connected with the oil inlet of the hydraulic control proportional valve 2.3, and the oil outlet of the hydraulic control proportional valve 2.3 is connected with the flow release oil port P.
The rotary motor is provided with a safety oil circuit: and a safety valve 2.1 is arranged in front of the flow release oil port P, and an outlet of the safety valve 2.1 is connected with the low-pressure oil way.
The rotary motor is provided with an oil supplementing way: the oil supplementing port M is connected with an inlet of the oil supplementing one-way valve 2.6, and an outlet of the oil supplementing one-way valve 2.6 is connected with the first cavity and the second cavity of the motor 2.7.
The opening pressure of the flow extraction switching valve 2.2 is adjustable, can be mechanically adjusted, can also be electrically controlled through a host controller, and is opened when the oil pressure at the inlet reaches the set opening pressure.
The set opening pressure of the safety valve 2.1 is determined by the rated pressure of each element and the rated pressure of the host system, when the oil pressure reaches the set opening pressure, the safety valve is opened, and the oil overflows to a low-pressure oil path and an oil return path of the host system, so that the oil pressure in the rotary motor is not more than the set opening pressure all the time.
The opening degree of the hydraulic control proportional valve 2.3 is determined by the hydraulic pressures of an internal spring, a first hydraulic control end and a second hydraulic control end: ① When the pressure of the oil inlet of the hydraulic control proportional valve 2.3 is smaller than the set opening pressure of the flow extraction switch valve 2.2, the flow extraction switch valve 2.2 is closed, so that the pilot pressures of the first hydraulic control end and the second hydraulic control end of the hydraulic control proportional valve 2.3 are the same, the valve core of the hydraulic control proportional valve 2.3 is in a closing position under the action of spring force, and the hydraulic energy of the system is fully used for supplying to the operation of the rotary motor without influencing the normal operation of the rotary motor. ② When the oil inlet pressure of the hydraulic control proportional valve 2.3 is larger than the set opening pressure of the flow extraction switch valve 2.2, the flow extraction switch valve 2.2 is opened, the opening degree of the hydraulic control proportional valve 2.3 is increased along with the increase of the oil inlet pressure of the hydraulic control proportional valve 2.3 and the opening pressure difference of the flow extraction switch valve 2.2, and is reduced along with the decrease of the oil inlet pressure of the hydraulic control proportional valve 2.3 and the opening pressure difference of the flow extraction switch valve 2.2. Therefore, when the system is started and braked in a revolving way, obvious pressure difference is generated at the two sides of the throttle orifice 2.4, and meanwhile, obvious pressure difference is generated at the first hydraulic control end and the second hydraulic control end of the hydraulic control proportional valve 2.3, so that the opening degree of the hydraulic control proportional valve 2.3 is increased, hydraulic energy can be recovered through the hydraulic control proportional valve 2.3 and the flow release oil port P, overflow during the starting of the revolving can be prevented, kinetic energy generated during the braking of the revolving can be recovered, and the power consumption of the system is reduced; when the rotation is accelerated and the rotation is approximately uniform, the pressure difference at the two sides of the throttle orifice 2.4 is smaller, the opening degree of the hydraulic control proportional valve 2.3 is small, and the hydraulic energy of the system is basically used for supplying the rotation motor to operate.
The energy loss of the hydraulic control proportional valve 2.3 is mainly that the hydraulic control port overcomes the spring force loss, is usually below 2Mpa, is far lower than the energy loss of an overflow valve of a conventional rotary motor system, and is extremely low.
The specific implementation modes of various functions of the rotary motor are as follows:
1) Buffering
When the construction machine is fully loaded and rotated, the moment of inertia of the boarding vehicle is very large, and when the motor 2.7 is started, braked or suddenly commutated, a great impact is caused on the hydraulic system, vibration and noise are generated, and even hydraulic elements are damaged.
At this time, the pressure of the first cavity of the motor 2.7 is higher, the pilot operated proportional valve 2.3 is opened, high-pressure oil is released through the pilot operated proportional valve 2.3 and the flow release oil port P, the pressure of the first cavity of the motor 2.7 is reduced, the opening degree of the pilot operated proportional valve 2.3 is positively correlated with the flow, abrupt change does not occur, the main loop obtains stable liquid flow, and a good buffering effect is achieved.
2) Rebound prevention
When the rotary motor is braked, the rotary motor continuously rotates for a certain angle in the original movement direction under the action of inertia, and the oil pressure of a certain chamber can be increased due to the compression of the volume of the chamber, so that the rotary motor generates a counter-rotation trend, namely rebound.
At this time, the pilot operated proportional valve 2.3 is opened, the high pressure oil is released through the pilot operated proportional valve 2.3 and the flow release port P, and the pressure of the first cavity of the motor 2.7 is reduced. The second cavity of the motor is supplemented with oil through an oil supplementing loop, and the pressures of the two cavities are rapidly balanced, so that the rebound prevention effect is achieved.
3) Oil supplementing anti-idle rotation of low-pressure cavity
When the rotary motor is braked, the rotary motor can continuously rotate for a certain angle in the original movement direction under the action of inertia, the oil pressure of a cavity is reduced due to the increase of the volume of the cavity, and even the tendency of idle running and negative pressure formation is caused, so that the service life of the element is influenced.
Therefore, the rotary motor is provided with an oil supplementing loop, the two cavities are connected with the total oil return path of the carrying host machine through the oil supplementing one-way valve 2.6, and oil can be quickly supplemented under the action of the main oil return back pressure of the host machine when the pressure of the cavity is low.
4) Pressure cut-off (protection) when internal pressure exceeds limit
The set opening pressure of the safety valve 2.1 is determined by the rated pressure of each element and the rated pressure of the carried host system, the safety valve is opened when the oil pressure reaches the set opening pressure, and the oil overflows to the oil return path through the low-pressure oil path, so that the oil pressure in the rotary motor is always not greater than the set opening pressure, and the safety valve plays a role in protection when the internal pressure exceeds the limit.
5) Starting anti-overflow flow
At the moment of turning start, the motor 2.7 has no rotating speed and no flow is needed, and the onboard host machine starts to supply oil to the motor 2.7. When the oil supply increases, a very high pressure builds up instantaneously inside the motor 2.7, and the flow extraction switching valve 2.2 opens. When the flow exceeds a certain degree, the pressure difference at two sides of the throttle orifice 2.4 is large to a certain degree, the valve core of the hydraulic control proportional valve 2.3 overcomes the spring force and moves towards the direction with large opening under the action of the hydraulic control force, the larger the flow is, the larger the opening is, the flow passes through the hydraulic control proportional valve 2.3 to the flow release oil port P, and the larger the flow is, the larger the flow of the hydraulic control proportional valve is, so that the self-adaptive internal closed loop adjustment process is realized.
When the rotary motor is started, the rotating speed is low, the required flow is small, and when the supplied flow of the carrying host is larger than the required flow, a higher pressure is established, and the flow extraction switch valve 2.2 is opened. Compared with the rotation starting stage, part of flow is supplied to the motor 2.7, the flow at the oil inlet of the hydraulic control proportional valve is less than the rotation starting stage, the opening is smaller than the rotation starting stage, and the flow is released from the flow release oil port P through the hydraulic control proportional valve 2.3, and meanwhile, the first cavity of the motor 2.7 can still keep higher pressure and maintain rotation acceleration. The rotation speed of the motor 2.7 is high in the later period of the rotation acceleration process, the required flow is more, the internal pressure of the motor 2.7 is further reduced, the flow extraction switch valve 2.2 is closed, the hydraulic control proportional valve 2.3 is closed, and the system flow is fully supplied to the motor 2.7.
The flow is released from the flow release oil port P through the hydraulic control proportional valve 2.3, and the energy consumption is far lower than that of a conventional system overflow valve.
6) Braking energy recovery
The engineering machinery rotating platform and the working device have large mass, moment of inertia and moment of inertia, and the rotation can not be stopped immediately due to the inertia effect during rotation braking, but can continue to rotate for a certain angle in the original motion state. The second cavity oil of the motor 2.7 is compressed, the pressure suddenly rises to a higher value, the flow extraction switch valve 2.2 is opened, the hydraulic control proportional valve 2.3 is opened, and the flow is discharged from the flow release oil port P through the hydraulic control proportional valve 2.3.
The flow is released from the flow release oil port P through the hydraulic control proportional valve 2.3, and the energy consumption is far lower than that of a conventional system overflow valve.
7) Maximum working torque controllable (temporary boost)
When the pressure of the first main oil way and the second main oil way of the rotary motor exceeds the set opening pressure of the flow extraction switching valve 2.2, the hydraulic control proportional valve 2.3 is opened, and hydraulic oil is released to the flow release oil port P, so that the highest working pressure of the system is balanced with the set opening pressure of the flow extraction switching valve 2.2.
During normal operation, the set opening pressure of the flow extraction switch valve 2.2 can be adjusted to the set pressure of the overflow valve of the conventional rotary motor, namely, the set pressure is lower than 28 Mpa.
When the system rotates in an ascending slope, starts under load and the like, the set opening pressure of the flow extraction switching valve 2.2 can be temporarily increased to the rated pressure of the system, namely about 34Mpa, the highest working pressure of the system is increased, and the load requirement is met.
While the utility model has been described with reference to certain preferred embodiments, it will be understood by those skilled in the art that various changes and modifications may be made and equivalents may be substituted for elements thereof without departing from the scope of the utility model. Therefore, any simple modification, equivalent variation and modification of the above embodiments according to the technical substance of the present utility model shall fall within the scope of the technical solution of the present utility model.
Claims (7)
1. The utility model provides an engineering machine tool hydraulic pressure gyration motor, includes motor body (2), set up main hydraulic fluid port A, main hydraulic fluid port B, oil compensating mouth M on the motor body, the motor is internal to set up motor (2.7), the motor has first chamber and second chamber, main hydraulic fluid port A communicates through first main oil circuit first chamber, main hydraulic fluid port B communicates through second main oil circuit second chamber, its characterized in that: an energy recovery module is arranged between the first main oil way and the second main oil way, a flow release oil port P is arranged on the motor body, the energy recovery module comprises an inlet end, an outlet end, a hydraulic control proportional valve (2.3), a flow extraction switch valve (2.2) and a throttle port (2.4), the inlet end is communicated with the first main oil way and the second main oil way, the outlet end is communicated with the flow release oil port P, the hydraulic control proportional valve is provided with a first hydraulic control end, a second hydraulic control end, an oil inlet and an oil outlet, the first hydraulic control end is communicated with the inlet end, the second hydraulic control end is communicated with the inlet end through the throttle port, the oil inlet is communicated with the inlet end, the oil outlet is communicated with the outlet end, the throttle port and the second hydraulic control end are simultaneously communicated with the inlet of the flow extraction switch valve, the outlet of the flow extraction switch valve is communicated with the oil supplementing port M, and when the pressure of the oil inlet of the hydraulic control proportional valve is smaller than the opening pressure of the flow extraction switch valve, the hydraulic control switch valve is closed; when the pressure of the oil inlet of the hydraulic control proportional valve is larger than the opening pressure of the flow extraction switching valve, the flow extraction switching valve is opened, the opening degree of the hydraulic control proportional valve is increased along with the increase of the pressure difference between the oil inlet of the hydraulic control proportional valve and the opening pressure of the flow extraction switching valve, and is reduced along with the decrease of the pressure difference between the oil inlet of the hydraulic control proportional valve and the opening pressure of the flow extraction switching valve.
2. The hydraulic swing motor according to claim 1, wherein the energy recovery module further comprises an anti-reverse flow check valve (2.5) mounted at the inlet end of the energy recovery module.
3. The hydraulic swing motor according to claim 1, wherein the energy recovery module further comprises a safety valve (2.1) mounted at the outlet end of the energy recovery module.
4. The hydraulic swing motor according to claim 1, wherein said orifice is replaced with a throttle valve.
5. The hydraulic swing motor according to claim 1, wherein an oil supplementing one-way valve is installed between the first main oil path and the second main oil path, an inlet of the oil supplementing one-way valve is communicated with the oil supplementing port M, and an outlet of the oil supplementing one-way valve is communicated with the first cavity and/or the second cavity of the motor.
6. The hydraulic swing motor according to claim 1, wherein the motor body is further provided with an oil drain Dr, and an inner end of the oil drain Dr is communicated with the motor.
7. A construction machine comprising the hydraulic swing motor of the construction machine according to any one of claims 1 to 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322997905.8U CN221074483U (en) | 2023-11-07 | 2023-11-07 | Engineering machinery hydraulic rotary motor and engineering machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322997905.8U CN221074483U (en) | 2023-11-07 | 2023-11-07 | Engineering machinery hydraulic rotary motor and engineering machinery |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN221074483U true CN221074483U (en) | 2024-06-04 |
Family
ID=91250093
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202322997905.8U Active CN221074483U (en) | 2023-11-07 | 2023-11-07 | Engineering machinery hydraulic rotary motor and engineering machinery |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN221074483U (en) |
-
2023
- 2023-11-07 CN CN202322997905.8U patent/CN221074483U/en active Active
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN201363332Y (en) | Large inertia variable frequency volume bypass throttling speed governing system | |
| CN103148031B (en) | Hydraulic movable arm loop energy-saving control system | |
| US8502402B2 (en) | Power generating apparatus of renewable energy type and control method thereof | |
| CN102912823B (en) | Rotary energy saving system of excavator | |
| KR101390078B1 (en) | Hybrid excavator boom actuator system and control method thereof | |
| WO2007081279A1 (en) | Control system for a work machine and method for controlling a hydraulic cylinder | |
| CN101688384A (en) | The engine control system of building machinery | |
| CN107965479B (en) | Quick compensation mechanism of mechanical-hydraulic composite energy and energy-saving electro-hydraulic system | |
| CN108894274B (en) | Excavator gyration energy recuperation and system of recycling | |
| CN111649023B (en) | Buffering oil supplementing system and method for electro-hydraulic double-control motor driving rotation system | |
| CN102030266A (en) | Crane and hydraulic control system thereof | |
| CN101718200B (en) | Shield cutter rotary drive pressure adapting hydraulic control system of proportional valve controlled energy accumulator | |
| CN221074483U (en) | Engineering machinery hydraulic rotary motor and engineering machinery | |
| CN108953309B (en) | Energy recovery and recycling hydraulic system | |
| CN114165490A (en) | Control method and system for controlling arm support to retract, mechanical equipment and storage medium | |
| CN112283190B (en) | Hydraulic system, hydraulic slewing mechanism and walking device | |
| CN112160949B (en) | Explosion-proof high-efficiency hydraulic pile hammer control system and pile driving method thereof | |
| CN201914850U (en) | Crane and hydraulic control system thereof | |
| CN204898749U (en) | Excavator hydraulic system with energy repayment function | |
| CN201116558Y (en) | Prime motor output torque balance control device | |
| CN106870482B (en) | The vibration hydraulic system of cement pavement resonance rock crushing plant | |
| CN110107560A (en) | Rotary blade type hydraulic steering gear | |
| CN214742496U (en) | Electric control hydraulic braking system with speed regulation and buffering functions for monorail crane | |
| CN213744202U (en) | Control system of hydraulic cylinder and excavator | |
| CN107420356A (en) | A kind of energy-saving hydraulic pumping plant for TRT fast cut valves |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |