CN118423251B - Self-adaptive booster oil pump system, hydraulic system, working machine and new energy vehicle - Google Patents
Self-adaptive booster oil pump system, hydraulic system, working machine and new energy vehicle Download PDFInfo
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- CN118423251B CN118423251B CN202410855958.2A CN202410855958A CN118423251B CN 118423251 B CN118423251 B CN 118423251B CN 202410855958 A CN202410855958 A CN 202410855958A CN 118423251 B CN118423251 B CN 118423251B
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- 230000007246 mechanism Effects 0.000 claims description 23
- 238000005452 bending Methods 0.000 claims description 14
- 238000005086 pumping Methods 0.000 claims description 13
- 230000005540 biological transmission Effects 0.000 claims description 10
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 238000010521 absorption reaction Methods 0.000 claims description 5
- 230000009471 action Effects 0.000 claims description 3
- 239000002828 fuel tank Substances 0.000 claims 1
- 230000005856 abnormality Effects 0.000 abstract description 7
- 238000010438 heat treatment Methods 0.000 abstract description 5
- 238000000926 separation method Methods 0.000 description 8
- 230000001105 regulatory effect Effects 0.000 description 3
- 239000002699 waste material Substances 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- WHXSMMKQMYFTQS-UHFFFAOYSA-N Lithium Chemical compound [Li] WHXSMMKQMYFTQS-UHFFFAOYSA-N 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 229910052744 lithium Inorganic materials 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
- F04B23/106—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being an axial piston pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/12—Combinations of two or more pumps the pumps being of different types at least one pump being of the rotary-piston positive-displacement type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
The application relates to the field of hydraulic pressure, and discloses a self-adaptive booster oil pump system, a hydraulic system, a working machine and a new energy vehicle, wherein the oil pump system comprises: a rotating shaft; the main pump is driven by the rotating shaft and is provided with a main oil suction port and a main oil discharge port; the booster pump can be driven by the rotating shaft and is provided with a booster oil suction port and a booster oil discharge port; the oil circuit assembly comprises a main oil suction oil circuit connected with the main oil suction port and a pressurizing oil discharge oil circuit connected with the pressurizing oil discharge port and the main oil suction oil circuit; and a clutch provided between the rotation shaft and the booster pump and capable of engaging or disengaging the rotation shaft and the booster pump. The application can greatly improve the overall energy efficiency of the oil pump system with the booster pump under the low-speed working condition, reduce the heating of the oil pump system, and avoid cavitation and noise abnormality phenomena caused by the oil pump system under the high-speed working condition, thereby ensuring that the oil pump system has excellent performance under the working conditions of different rotating speeds.
Description
Technical Field
The application belongs to the technical field of hydraulic pressure, and particularly relates to an oil pump system with self-adaptive supercharging, a hydraulic system, a working machine and a new energy vehicle.
Background
In a hydraulic system, the volume of the oil pump can be effectively reduced by reducing the displacement of the oil pump and improving the rotation speed of the oil pump, so that the hydraulic system is more suitable for various host systems which are compactly arranged. Meanwhile, the application of the high-speed motor is promoted by the rapid development of electrification, and the high-speed oil pump suitable for the high-speed motor has a wider application prospect.
Taking a hydraulic plunger pump as an example, the main factor limiting the increase of the rotation speed of the hydraulic plunger pump is the self-priming performance, and the inlet pressure of the oil of the plunger pump is usually required to be higher than the air separation pressure of the oil so as to avoid cavitation. When the self-priming plunger pump is too high in rotating speed and large in flow demand, the pressure difference between the inlet pressure of the oil pump and the atmospheric pressure is increased, and the pressure is easily reduced to be lower than the air separation pressure, so that cavitation is generated. Therefore, the common plunger pump ensures the service life of the oil pump by limiting the maximum rotation speed to avoid cavitation.
In order to increase the rotation speed of the oil pump and avoid cavitation caused by the fact that the pressure of oil entering the plunger pump is lower than the air separation pressure, a booster pump is used for increasing the inlet pressure of the plunger pump so as to achieve the purpose of increasing the rotation speed of the oil pump. However, when the existing oil pump system for increasing the inlet pressure of the plunger pump through the booster pump is operated under the low-pressure and low-speed working condition, the oil pump system is extremely low in overall efficiency, and has the problem of large heating value, so that the overall energy efficiency of the oil pump system is extremely low, and the service life is adversely affected.
Disclosure of Invention
The application aims to provide an oil pump system, a hydraulic system, a working machine and a new energy vehicle which are self-adaptively pressurized, so that the overall energy efficiency of the oil pump system with a booster pump under a low-speed working condition can be greatly improved, the heating of the oil pump system can be reduced, and cavitation and noise abnormal phenomena caused by the oil pump system under a high-speed working condition can be avoided.
In order to achieve the above object, an aspect of the present application provides an oil pump system comprising:
A rotating shaft;
the main pump is driven by the rotating shaft and is provided with a main oil suction port and a main oil discharge port;
the booster pump can be driven by the rotating shaft and is provided with a booster oil suction port and a booster oil discharge port;
the oil circuit assembly comprises a main oil suction oil circuit connected with the main oil suction port and a pressurizing oil discharge oil circuit connected with the pressurizing oil discharge port and the main oil suction oil circuit; and
A clutch provided between the rotation shaft and the booster pump and capable of engaging or disengaging the rotation shaft and the booster pump;
Under the low-speed working condition that the rotating speed of the rotating shaft is smaller than the preset critical rotating speed, the clutch separates the rotating shaft from the booster pump, and the main pump absorbs oil through the main oil absorption oil way; and under the high-speed working condition that the rotating speed of the rotating shaft is not less than the preset critical rotating speed, the clutch is connected with the rotating shaft and the booster pump, and the main pump boosts the oil absorption through the booster pump.
In some embodiments, the oil circuit assembly further comprises an anti-suction valve connected in series in the pressurized oil drain circuit and provided with a first opening pressure;
Under the working condition that the oil pressure of the pressurizing oil discharge oil way is smaller than the first opening pressure, the anti-suction valve is in a shut-off state; and under the working condition that the oil pressure of the pressurizing oil discharge oil way is not smaller than the first opening pressure, the anti-suction valve is in a conducting state.
In some embodiments, the oil circuit assembly further comprises a check valve connected in series in the main oil suction circuit, a stop end of the check valve being connected with the pressure increasing oil discharge circuit.
In some embodiments, the oil circuit assembly further comprises a boost oil suction circuit connected to the boost oil suction port, the boost oil suction circuit being connected to the conducting end of the check valve.
In some embodiments, the oil circuit assembly further comprises a boost pressure control valve provided with an adjustable second opening pressure, and one end of the boost pressure control valve is respectively connected with the boost oil discharge oil circuit and the main oil suction port.
In some embodiments, the clutch is disposed between the main pump and the booster pump.
In some embodiments, the clutch comprises an input hub, an output hub and a plurality of elastic throwing block mechanisms, the input hub is fixedly sleeved on the rotating shaft, the plurality of elastic throwing block mechanisms are sequentially arranged on the outer periphery of the input hub at intervals along the circumferential direction, the output hub is sleeved outside the input hub at intervals and is connected with the booster pump, a plurality of clamping grooves are sequentially arranged on the inner peripheral wall of the output hub along the circumferential direction, and each elastic throwing block mechanism comprises a centrifugal throwing block and elastic bending pieces, and two ends of each elastic bending piece are respectively connected with the centrifugal throwing block and the input hub; under the low-speed working condition, the centrifugal throwing block is separated from the clamping groove; under the high-speed working condition, the centrifugal throwing block can overcome the elastic force of the elastic bending piece to move under the action of centrifugal force so as to be clamped in the clamping groove.
In some embodiments, the rotating shaft comprises a power shaft and a transmission shaft, the main pump is further provided with a main oil distribution disc and a pumping mechanism, the main oil suction port and the main oil discharge port are both arranged on the main oil distribution disc, the booster pump is further provided with a booster oil distribution disc and a rotor, and the booster oil suction port and the booster oil discharge port are both arranged on the booster oil distribution disc;
The transmission shaft and the pumping mechanism are hinged with the power shaft, the supercharging oil distribution disc, the rotor, the main oil distribution disc and the pumping mechanism are sequentially arranged on the transmission shaft along the axial direction, and the clutch is arranged between the transmission shaft and the rotor.
In some embodiments, the main oil distribution disc is abutted with the rotor to form an end face, and an oil distribution groove is formed on the end face of the main oil distribution disc facing the rotor and is communicated with the internal oil duct of the booster pump.
In some embodiments, the oil pump system further comprises a housing, wherein the shaft, the main pump, the booster pump, the oil circuit assembly, and the clutch are all disposed within the housing.
In some embodiments, the booster pump is a vane pump; and/or the main pump is a self-priming plunger pump.
The second aspect of the present application also provides a hydraulic system comprising:
An oil tank;
A power device; and
According to the oil pump system, the pressurizing oil suction port and the main oil suction port are connected with the oil tank, and the rotating shaft is driven by the power device.
The third aspect of the present application also provides a work machine comprising the hydraulic system described above.
The fourth aspect of the application also provides a new energy vehicle, which comprises the hydraulic system and a power battery for supplying power to the hydraulic system.
According to the technical scheme, the oil pump system can adjust the state of the clutch according to different rotating speed working conditions, for example, when the rotating shaft drives the main pump to run at a low speed, the flow requirement of the main pump is smaller, and the pressure difference between the inlet oil pressure of the main pump and the atmospheric pressure is smaller, so that the inlet oil pressure is not lower than the air separation pressure to cause cavitation and noise abnormality, and therefore, under the low-speed working condition, the rotating shaft can be separated from the booster pump through the clutch without booster pump pressurization, so that the driving energy waste caused by the continuous running of the booster pump and the overall efficiency of the oil pump system under the low-speed working condition are avoided, the mechanical loss and the hydraulic overflow loss of the booster pump are reduced, the overall energy efficiency of the oil pump system under the low-speed working condition is improved, the heating of the oil pump system is reduced, and the service life of the oil pump system is prolonged. For example, when the rotating shaft drives the main pump to run at a high speed, the rotating shaft is connected with the booster pump through the clutch, so that the rotating shaft drives the main pump and the booster pump to run synchronously, and oil in the oil pump system enters the main pump from the booster pump oil discharge oil way and the main oil suction port after being boosted by the booster pump, so that cavitation and noise abnormality caused by the fact that the inlet oil pressure of the main pump is lower than the air separation pressure are effectively avoided. In general, the application can enable the oil pump system to have excellent performance under different rotating speed working conditions.
Additional features and advantages of embodiments of the application will be set forth in the detailed description which follows.
Drawings
The accompanying drawings are included to provide a further understanding of embodiments of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain, without limitation, the embodiments of the application. Other figures may be made from the structures shown in these figures without inventive effort for a person of ordinary skill in the art. In the drawings:
FIG. 1 is a schematic illustration of a hydraulic system according to an embodiment of the present application;
FIG. 2 is a schematic diagram of an oil pump system according to an embodiment of the present application;
FIG. 3 is a schematic illustration of a clutch in accordance with an embodiment of the application.
Description of the reference numerals
10 Main pump 20 clutch
30 Booster pump 40 anti-suction valve
50 Check valve 60 oil tank
70 Boost pressure control valve 80 valve group
90 Power shaft 100 transmission shaft
110 Front pump casing 120 rear pump casing
130 Oil seal 140 bearing
150 Power plant 160 universal joint
101 Plunger 102 cylinder
103 Main oil distribution disc 201 input hub
202 Output hub 203 centrifugal fling block
204 Elastic bending piece 301 rotor
302 Booster oil distribution disc
Detailed Description
The following describes specific embodiments of the present application in detail with reference to the drawings. It should be understood that the detailed description and specific examples, while indicating and illustrating the application, are not intended to limit the application.
Referring to fig. 1 to 3, a first exemplary embodiment of the present application provides an oil pump system capable of adaptively boosting, more specifically, capable of adaptively boosting based on a rotational speed, which includes a rotary shaft, a main pump 10, a booster pump 30, an oil path assembly, and a clutch 20.
Specifically, when the rotary shaft inputs power from the outside of the oil pump system, the rotary shaft drives the main pump 10 to operate, and can drive the booster pump 30 to operate. The main pump 10 is operated by sucking oil through its main oil suction port, pressurizing the oil in the pump, and pumping out the pressurized oil through its main oil discharge port (e.g., to a hydraulic actuator to drive it). When the booster pump 30 operates, oil can be sucked from the outside of the oil pump system through the booster oil suction port, the oil is pressurized in the pump, and then the booster oil pump is led to the main oil suction port of the main pump 10 through the booster oil discharge port, so that the pressure boost of the inlet oil pressure of the main pump 10 can be realized.
Further, the main pump 10 of the present application has more than one oil suction path. In the oil way assembly, a main oil suction oil way connected with the main oil suction port and a pressurizing oil discharge oil way connected with the pressurizing oil discharge port and the main oil suction oil way are arranged, so that the main oil suction port can suck oil from the outside of the oil pump system through the oil inlet end of the main oil suction oil way, and can suck the pressurizing oil into the main oil suction oil way through the pressurizing oil discharge oil way.
The clutch 20 provided by the application can realize that the main pump 10 can switch between the two oil suction paths, and the clutch 20 is arranged between the rotating shaft and the booster pump 30 and can connect or disconnect the rotating shaft and the booster pump 30.
When the clutch 20 engages the rotating shaft with the booster pump 30, the rotating shaft drives the main pump 10 and the booster pump 30 to operate synchronously, and at this time, the booster pump 30 can introduce the pressurized oil into the main oil suction passage through the pressurized oil discharge passage, and then the main oil suction passage introduces the pressurized oil into the main pump 10.
When the clutch 20 separates the rotation shaft from the booster pump 30, the rotation shaft drives the main pump 10 to operate, the booster pump 30 is stopped without power input, at this time, the main pump 10 sucks oil from the outside of the oil pump system through the oil inlet end of the main oil suction passage, and the booster pump 30 does not perform a boosting function.
Based on the above arrangement, the oil pump system of the present application can adjust the state of the clutch 20 according to different rotational speed conditions, for example, when the rotating shaft drives the main pump 10 to run at a low speed, the flow requirement of the main pump 10 is smaller, and the pressure difference between the inlet oil pressure of the main pump 10 and the atmospheric pressure is smaller, so that the inlet oil pressure is not lower than the air separation pressure to cause cavitation and noise abnormality, so that the rotating shaft and the booster pump 30 can be separated by the clutch 20 under the low speed condition without the booster pump 30 to boost, so that the driving energy waste and the overall efficiency of the oil pump system under the low speed condition (the overall efficiency of the existing oil pump system is the product of the efficiency of the serially connected main pump and booster pump, and the efficiency of the existing booster pump under the low speed condition is extremely low, thereby causing the overall efficiency of the oil pump system under the low speed condition) are reduced, the overall energy efficiency of the booster pump 30 under the low speed condition is improved, the heating is reduced, and the service life is prolonged.
For another example, when the rotating shaft drives the main pump 10 to run at a high speed, the rotating shaft can be engaged with the booster pump 30 through the clutch 20, so that the rotating shaft drives the main pump 10 and the booster pump 30 to run synchronously, and at the moment, oil in the oil pump system enters the main pump from the booster oil discharging oil way and the main oil suction port after being boosted by the booster pump 30, so that cavitation and noise abnormality phenomena caused by that the inlet oil pressure of the main pump 10 is lower than the air separation pressure are effectively avoided.
In general, the application can enable the oil pump system to have excellent performance under different rotating speed working conditions.
It should be noted that the present application does not limit the oil pump system to engage the clutch 20 under the high-speed condition and disengage the clutch 20 under the low-speed condition, but can switch the state of the clutch 20 in due course based on the actual condition.
In some embodiments, the critical point (i.e. preset critical rotation speed) of the high-low speed working condition can be preset in advance by people, and then the structural form, parameters, control opportunities and the like of the clutch 20 are designed on the premise that the critical point is preset, so that the clutch 20 separates the rotating shaft from the booster pump 30 under the low-speed working condition that the rotation speed of the rotating shaft is less than the preset critical rotation speed, the main pump 10 absorbs oil only through the main oil absorption oil path, and the clutch 20 engages the rotating shaft and the booster pump 30 under the high-speed working condition that the rotation speed of the rotating shaft is not less than the preset critical rotation speed, so that the main pump 10 pressurizes and absorbs oil through the booster pump 30.
In other words, by designing the structural form and parameters of the clutch 20 or adopting the modes of linkage control of the controller and the rotation speed sensor, the clutch 20 can have the function of switching the engagement and disengagement states at a speed, so that the oil pump system can accurately and flexibly switch the operation mode according to the rotation speed.
More specifically, for example, when the on-off of the clutch 20 needs to be controlled by adopting the mode of linkage control of the controller and the rotation speed sensor, the rotation speed sensor can be utilized to detect the rotation speed of the rotation shaft in real time and transmit data to the controller, and a preset critical rotation speed value is pre-stored in the controller and can be compared with the rotation speed of the rotation shaft. When the controller judges that the rotating speed of the rotating shaft is smaller than the preset critical rotating speed, the controller controls the clutch 20 to be separated; when the controller determines that the rotational speed of the rotational shaft is not less than the preset threshold rotational speed, the controller controls the clutch 20 to be engaged.
An example of adjusting the preset threshold rotational speed by adjusting the structural configuration and parameters of the clutch 20 will be described later with reference to fig. 3, which is not described herein.
In some embodiments, referring to fig. 2, the oil circuit assembly further includes a valve block 80, the valve block 80 being shown for illustrative purposes only and not to show the specific configuration of the valve structure shown, namely the anti-suction valve 40 or the check valve 50 and the boost pressure control valve 70, which will be described later. In addition, the anti-suction valve 40 and the check valve 50 and the boost pressure control valve 70, which will be described later, are not necessarily integrated in the form of the valve block 80, but may be separately provided, and the present application is not limited thereto.
The valve block 80 may include an anti-suction valve 40 connected in series in the pressurized drain line and having a first opening pressure. Under the condition that the oil pressure of the boost oil discharge passage is smaller than the first opening pressure, the anti-suction valve 40 is in the shut-off state, and the booster pump 30 does not input the boost oil whose oil pressure does not meet the minimum requirement (i.e., the oil pressure value equivalent to the first opening pressure) into the main pump 10. Under the working condition that the oil pressure of the pressurizing oil discharge passage is not less than the first opening pressure, the anti-suction valve 40 is in a conducting state, and at this time, the pressurizing pump 30 can input the pressurizing oil with the oil pressure meeting the minimum requirement into the main pump 10, so as to pressurize the inlet oil pressure of the main pump 10.
By providing the anti-suction valve 40, it is ensured that the booster pump 30 does not input the pressurized oil whose oil pressure does not meet the minimum requirement into the main pump 10, thereby more effectively avoiding cavitation and noise abnormality caused by air suction of the main pump 1, and further improving the anti-suction capability of the oil pump system.
It should be noted that the present application is not limited to the specific type of the anti-suction valve 40, for example, a spring check valve as shown in fig. 1, or an overflow valve, a sequence valve, etc. may be used, and different types may be selected according to the actual working condition requirements.
In some embodiments, valve block 80 may include a check valve 50 in series with the main charge oil passage, with the blocked end of check valve 50 connected to the charge oil discharge passage. When the clutch 20 is engaged and the booster pump 30 transfers the pressurized oil into the main oil suction passage through the pressurized oil discharge passage, the pressurized oil transferred into the main oil suction passage applies a closing force to the cut-off end of the check valve 50, so that the check valve 50 cannot be opened at this time, and the check valve 50 can prevent the pressurized oil transferred into the main oil suction passage from reversely flowing out of the oil inlet end of the main oil suction passage, thereby avoiding the inlet oil pressure loss of the main pump 10, further ensuring that the inlet oil pressure is not lower than the air separation pressure, and further reducing the risk of cavitation and noise abnormality.
Further, the oil path assembly further includes a pressurizing oil suction path connected to the pressurizing oil suction port, and the pressurizing oil suction path is connected to the conducting end of the check valve 50. In this way, the oil pump system can suck oil only through the oil intake end of the main oil suction passage, and when the booster pump 30 is not operated, the oil sucked from the oil intake end of the main oil suction passage enters the main pump 10 through the check valve 50. When the booster pump 30 is operated, the oil sucked from the oil inlet end of the main oil suction passage enters the booster pump 30 through the booster oil suction passage. At this time, the oil supply structure (such as an oil tank) outside the oil pump system is provided with only an oil port connected to the oil inlet end of the main oil suction passage, so that the main pump 10 and the booster pump 30 can be supplied with oil.
It should be noted that the present application is not limited to the specific type of the check valve 50, for example, a single check valve as shown in fig. 1 may be used, or other valves such as a sequence valve may be used as the check valve, and different types may be selected according to the actual working condition requirements.
In some embodiments, the valve block 80 may include a boost pressure control valve 70 provided with an adjustable second opening pressure, one end of the boost pressure control valve 70 being connected to the boost drain passage and the main suction port of the main pump 10, respectively. When the booster pump 30 is operated, after the pressurized oil in the pressurized oil discharge passage merges into the main oil suction passage, if the inlet pressure of the main pump 10 is smaller than the second opening pressure of the boost pressure control valve 70, the inlet pressure may continue to rise; if the inlet pressure of the main pump 10 is not less than the second opening pressure, the boost pressure control valve 70 opens to release pressure, so that the inlet pressure of the main pump 10 can be maintained equal to the second opening pressure by setting the boost pressure control valve 70, and the inlet pressure of the main pump 10 can be regulated due to the adjustable second opening pressure, so that the inlet pressure of the main pump 10 can be timely and accurately regulated according to the actual working conditions, so as to adapt to more different working conditions.
By contrast, the oil drain port of the booster pump in the prior art is directly connected with the oil suction port of the main pump, and the booster pump adopts the impeller type centrifugal pump, so that the oil drain oil pressure of the impeller type centrifugal pump cannot continuously rise after reaching the upper limit, the oil pressure upper limit value is determined by the impeller structure of the impeller type centrifugal pump, and the oil drain port cannot be flexibly regulated according to the pressurizing requirement of the main pump in the using and matching process, so that the condition of too high or too low pressurizing pressure is easily caused, and the energy loss or insufficient pressurizing is caused. The oil pump system of the application can flexibly adjust the boost pressure by arranging the boost pressure control valve 70 so as to adapt to different main pump characteristics and use conditions and improve the overall efficiency of the oil pump system.
It should be noted that the present application is not limited to the specific type of the boost pressure control valve 70, for example, a spring check valve with adjustable opening pressure as shown in fig. 1 may be used, or an overflow valve, a sequence valve, etc. may be used, and different types may be selected according to the actual requirements of working conditions.
In addition, the valve block 80 of the present application is not limited to the valve block that may include at least one of the above-described anti-suction valve 40, check valve 50, and boost pressure control valve 70, and may be integrally provided with other functions according to actual operating condition requirements. By adopting the form of the valve group 80, the integrated level is high, the disassembly and assembly are convenient, the compactness is strong, and the whole volume of the oil pump system is reduced.
In some embodiments, referring to fig. 2, a clutch 20 may be provided between the main pump 10 and the booster pump 30, making the structural arrangement of the oil pump system more compact.
Further, referring to fig. 3, the clutch 20 may include an input hub 201, an output hub 202, and a plurality of resilient slinger mechanisms. Specifically, the input hub 201 is fixedly sleeved on the rotating shaft, a plurality of elastic throwing block mechanisms are sequentially arranged on the outer periphery of the input hub 201 at intervals along the circumferential direction, the output hub 202 is sleeved outside the input hub 201 at intervals and is connected with the booster pump 30, a plurality of clamping grooves are sequentially formed in the inner peripheral wall of the output hub 202 along the circumferential direction, and each elastic throwing block mechanism comprises a centrifugal throwing block 203 which can be clamped in the clamping groove and elastic bending pieces 204 of which two ends are respectively connected with the centrifugal throwing block 203 and the input hub 201.
When the rotating shaft is stationary, the input hub 201 is also stationary, and at this time, the plurality of elastic slinger mechanisms do not move, and the input hub 201 and the output hub 202 are not connected.
When the rotating shaft rotates at a low speed, the input hub 201 rotates at a low speed correspondingly, at this time, the centrifugal throwing block 203 is thrown outwards by a small distance due to a small centrifugal force, the expansion amount of the bending angle of the elastic bending piece 204 is small, the centrifugal throwing block 203 cannot be clamped in the clamping groove of the inner peripheral wall of the output hub 202, and therefore the input hub 201 and the output hub 202 cannot be connected, and therefore the clutch 20 cannot transmit the power of the rotating shaft to the booster pump 30, and the booster pump 30 does not operate under a low-speed working condition.
When the rotating shaft rotates at a high speed, the input hub 201 also rotates at a corresponding high speed, at this time, the centrifugal throwing block 203 is thrown outwards by a larger distance due to a larger centrifugal force, the expansion amount of the bending angle of the elastic bending piece 204 is larger, and the centrifugal throwing block 203 can be clamped in the clamping groove of the inner peripheral wall of the output hub 202, so that the input hub 201 and the output hub 202 are relatively fixed, the output hub 202 rotates at a high speed in synchronization with the rotating shaft, and because the output hub 202 is connected with the booster pump 30, the clutch 20 can transmit the power of the rotating shaft to the booster pump 30 at this time, and the booster pump 30 runs under a high-speed working condition.
When the rotation speed of the rotation shaft is reduced, the centrifugal force applied to the centrifugal throwing block 203 is reduced, and at this time, the elastic bending piece 204 can drive the centrifugal throwing block 203 to separate from the clamping groove of the inner peripheral wall of the output hub 202 under the action of elastic restoring force, so that the connection between the input hub 201 and the output hub 202 is disconnected, and the clutch 20 cannot transmit the power of the rotation shaft to the booster pump 30, that is, the booster pump 30 stops running.
It should be noted that, when the value of the preset critical rotation speed needs to be adjusted, the preset critical rotation speed may be adjusted by changing the elastic bending piece 204 with different elastic moduli, the elastic bending piece 204 with different forms, the centrifugal slinger 203 with different weights, or the like (i.e. adjusting the structural form and parameters of the clutch 20).
In some embodiments, referring to fig. 2, the shaft includes a power shaft 90 and a drive shaft 100, the drive shaft 100 being hinged to the power shaft 90 (e.g., the drive shaft 100 may be hinged to the power shaft 90 via a universal joint 160), the power shaft being capable of inputting power from outside the oil pump system and driving the drive shaft 100 to rotate.
The main pump 10 is further provided with a main oil distribution plate 103 and a pumping mechanism hinged with the power shaft 90, and a main oil suction port and a main oil discharge port are both provided on the main oil distribution plate 103. After the oil enters the main oil suction port on the main oil distribution disc 103, the oil can be distributed into the pumping mechanism by the main oil distribution disc 103, and the pumping mechanism can discharge the pressure oil in the pumping mechanism outside through the main oil suction port on the main oil distribution disc 103.
Taking fig. 2 as an example, the main pump 10 may employ a self-priming plunger pump (and a diagonal plunger pump is shown) where the pumping mechanism includes a plunger 101 and a cylinder 102. Wherein, one end of the plunger 101 is hinged to the inner end of the power shaft 90 through a spherical hinge, and the other end of the plunger 101 slidably extends into the cylinder 102. When the power shaft 90 rotates, the plunger 101 and the cylinder 102 can be driven to rotate synchronously, and meanwhile, the plunger 101 can slide back and forth in the cylinder 102, so that oil can be pumped continuously.
The booster pump 30 is further provided with a booster oil distribution disc 302 and a rotor 301, and a booster oil suction port and a booster oil discharge port are both arranged on the booster oil distribution disc 302. After the oil enters the pressurizing oil suction port on the pressurizing oil distribution disc 302, the pressurizing oil distribution disc 302 can distribute the oil into a pump body (the pump body comprises a rotor 301) of the pressurizing pump 30, the pump body of the pressurizing pump 30 can discharge the pressurizing oil inside the pressurizing oil outside through the pressurizing oil discharge port of the pressurizing oil distribution disc 302, and then the pressurizing oil is conveyed to the main oil suction port on the main oil distribution disc 103 through a pressurizing oil discharge oil way and a main oil suction oil way, so that the inlet oil pressure of the main pump 10 is pressurized.
In addition, the booster oil distribution disc 302, the rotor 301, the main oil distribution disc 103 and the pumping mechanism in this embodiment are sequentially arranged on the transmission shaft 100 in the axial direction, so that the oil pump system has a compact structure, and a structural basis is provided for the series-connected oil pump which is integrally designed as an oil pump system and has a smaller size.
Further, the clutch 20 is provided between the drive shaft 100 and the rotor 301. When the clutch 20 is in the engaged state, the power of the drive shaft 100 may be transmitted to the rotor 301, so that the booster pump 30 may be driven to operate. When the clutch 20 is in the disengaged state, the power of the drive shaft 100 cannot be transmitted to the rotor 301, and at this time, the booster pump 30 stops operating. It can be seen that the arrangement of the clutch 20 in this embodiment is also beneficial to realizing compact and integrated design of the oil pump system.
Further, the main oil distribution disc 103 is abutted against the rotor 301, and an oil distribution groove is formed on the end surface of the main oil distribution disc 103 facing the rotor 301, and the oil distribution groove is communicated with the internal oil duct of the booster pump 30, so that the main oil distribution disc 103 can be used for distributing the internal oil of the booster pump 30 and the main pump 10 at the same time, and the oil pump system is multipurpose, so that the structure is more compact.
In some embodiments, with continued reference to FIG. 2, the oil pump system may further include a housing (e.g., may include a front pump housing 110 and a rear pump housing 120 as shown), and by disposing the above-described shaft, main pump 10, booster pump 30, oil circuit assembly, and clutch 20 within the housing, the oil pump system may be integrated as a single, smaller-sized tandem oil pump for quick installation and use in different hydraulic systems.
In addition, the above-mentioned tandem oil pump can be further provided with an oil seal 130, a bearing 140 and other components, so as to ensure the sealing performance of the oil pump and the rotation support of the power shaft 90.
In some embodiments, the booster pump 30 may be a vane pump, for example, a double-acting vane pump, and the volumetric efficiency of the booster pump 30 may be up to 95% or more, and in the case where the booster pump 30 is used in series with the main pump 10, the total efficiency of the oil pump system is the product of the efficiencies of the booster pump 30 and the main pump 10, so that compared with the existing impeller type centrifugal pump with the volumetric efficiency of only about 53%, the booster pump 30 has a substantially improved booster efficiency, and reduces heat generation, thereby greatly improving the overall efficiency of the oil pump system and reducing energy loss and waste.
It should be noted that, the main pump 10 of the present application is not limited to the plunger pump exemplified above, the booster pump 30 is not limited to the vane pump exemplified above, and any type of oil pump may be used for the main pump 10 and the booster pump 30 according to the actual working conditions. In other words, the present application is not limited to the specific type of the main pump 10 and the booster pump 30.
Referring again to fig. 1, a second exemplary embodiment of the present application also provides a hydraulic system including a tank 60, a power plant 150 (e.g., a high-speed motor, etc.), and the oil pump system described above. The pressurizing oil suction port and the main oil suction port of the oil pump system are connected with the oil tank 60, and the rotating shaft is driven by the power device 150. Obviously, the hydraulic system of the present application should have all the technical effects brought by the above-mentioned oil pump system, so that the description thereof is omitted here.
Further, a third exemplary embodiment of the present application provides a work machine including the hydraulic system described above. It is obvious that the working machine of the present application should also have all the technical effects brought by the oil pump system described above, and therefore, the description thereof will not be repeated here.
The working machine of the present application includes, but is not limited to, a construction machine, an agricultural machine, a working robot, etc., and the power of the working machine may be a new energy battery, a fuel engine, a hybrid device, a mechanism, etc.
The working machine of the present application may be a new energy vehicle such as a new energy vehicle, an automobile crane, a truck crane, a mixer truck, a pump truck, a fire truck, a road construction vehicle, an environmental sanitation vehicle, etc., and may supply power to a hydraulic system such as the power plant 150 in the hydraulic system by a power battery (e.g., lithium battery, hydrogen fuel cell) or the like.
In the description of the present application, it should be understood that the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present application, the meaning of "plurality" means at least two, for example, two, three, etc., unless specifically defined otherwise.
In the present application, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; may be mechanically connected, may be electrically connected or may be in communication with each other; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art according to the specific circumstances.
In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present application. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.
While embodiments of the present application have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the application, and that variations, modifications, alternatives and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the application.
Claims (14)
1. An oil pump system, comprising:
A rotating shaft;
a main pump (10) driven by the rotating shaft and provided with a main oil suction port and a main oil discharge port;
A booster pump (30) which can be driven by the rotating shaft and is provided with a booster oil suction port and a booster oil discharge port;
the oil circuit assembly comprises a main oil suction oil circuit connected with the main oil suction port and a pressurizing oil discharge oil circuit connected with the pressurizing oil discharge port and the main oil suction oil circuit; and
A clutch (20) provided between the rotation shaft and the booster pump (30) and capable of engaging or disengaging the rotation shaft and the booster pump (30);
Under the low-speed working condition that the rotating speed of the rotating shaft is smaller than a preset critical rotating speed, the clutch (20) separates the rotating shaft from the booster pump (30), and the main pump (10) absorbs oil through the main oil absorption oil way; under the high-speed working condition that the rotating speed of the rotating shaft is not less than the preset critical rotating speed, the clutch (20) is connected with the rotating shaft and the booster pump (30), and the main pump (10) boosts the oil absorption through the booster pump (30).
2. The oil pump system of claim 1, wherein the oil circuit assembly further comprises an anti-suction valve (40) connected in series in the pressurized oil discharge circuit and provided with a first opening pressure;
Under the working condition that the oil pressure of the pressurizing oil discharge oil way is smaller than the first opening pressure, the anti-suction valve (40) is in a shut-off state; and under the working condition that the oil pressure of the pressurizing oil discharge oil way is not smaller than the first opening pressure, the anti-suction valve (40) is in a conducting state.
3. The oil pump system of claim 1, wherein the oil circuit assembly further includes a check valve (50) connected in series in the main oil suction circuit, a shut-off end of the check valve (50) being connected to the pressurized oil discharge circuit.
4. The oil pump system of claim 3, wherein the oil circuit assembly further includes a pressurized oil suction circuit connected to the pressurized oil suction port, the pressurized oil suction circuit being connected to the conduction end of the check valve (50).
5. The oil pump system of claim 1, wherein the oil circuit assembly further includes a boost pressure control valve (70) provided with an adjustable second opening pressure, one end of the boost pressure control valve (70) being connected to the boost oil discharge oil circuit and the main oil suction port, respectively.
6. The oil pump system according to claim 1, characterized in that the clutch (20) is provided between the main pump (10) and the booster pump (30).
7. The oil pump system according to claim 6, wherein the clutch (20) comprises an input hub (201), an output hub (202) and a plurality of elastic throwing block mechanisms, the input hub (201) is fixedly sleeved on the rotating shaft, the plurality of elastic throwing block mechanisms are sequentially arranged on the outer periphery of the input hub (201) at intervals along the circumferential direction, the output hub (202) is sleeved outside the input hub (201) at intervals and is connected with the booster pump (30), a plurality of clamping grooves sequentially arranged along the circumferential direction are formed in the inner peripheral wall of the output hub (202), and each elastic throwing block mechanism comprises a centrifugal throwing block (203) and an elastic bending piece (204) with two ends respectively connected with the centrifugal throwing block (203) and the input hub (201); under the low-speed working condition, the centrifugal throwing block (203) is separated from the clamping groove; under the high-speed working condition, the centrifugal throwing block (203) can overcome the elasticity of the elastic bending piece (204) to move outwards under the action of centrifugal force so as to be clamped in the clamping groove.
8. The oil pump system according to claim 1, characterized in that the rotating shaft comprises a power shaft (90) and a transmission shaft (100), the main pump (10) is further provided with a main oil distribution disc (103) and a pumping mechanism, the main oil suction port and the main oil discharge port are both arranged on the main oil distribution disc (103), the booster pump (30) is further provided with a booster oil distribution disc (302) and a rotor (301), and the booster oil suction port and the booster oil discharge port are both arranged on the booster oil distribution disc (302);
The transmission shaft (100) and the pumping mechanism are hinged to the power shaft (90), the supercharging oil distribution disc (302), the rotor (301), the main oil distribution disc (103) and the pumping mechanism are sequentially arranged on the transmission shaft (100) along the axial direction, and the clutch (20) is arranged between the transmission shaft (100) and the rotor (301).
9. The oil pump system according to claim 8, wherein the main oil distribution pan (103) forms an end face abutment with the rotor (301), and an oil distribution groove is formed on an end face of the main oil distribution pan (103) facing the rotor (301), the oil distribution groove communicating with an internal oil passage of the booster pump (30).
10. The oil pump system of claim 1, further comprising a housing, wherein the shaft, the main pump (10), the booster pump (30), the oil circuit assembly, and the clutch (20) are all disposed within the housing.
11. The oil pump system according to any one of claims 1 to 10, wherein the booster pump (30) is a vane pump; and/or the main pump (10) is a self-priming plunger pump.
12. A hydraulic system, comprising:
A fuel tank (60);
A power unit (150); and
The oil pump system according to any one of claims 1 to 11, wherein the pressurizing oil suction port and the main oil suction port are both connected to the oil tank (60), and the rotating shaft is driven by the power device (150).
13. Work machine, characterized by comprising a hydraulic system according to claim 12.
14. New energy vehicle, characterized in that it comprises a hydraulic system according to claim 12 and a power battery for powering the hydraulic system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410855958.2A CN118423251B (en) | 2024-06-28 | 2024-06-28 | Self-adaptive booster oil pump system, hydraulic system, working machine and new energy vehicle |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202410855958.2A CN118423251B (en) | 2024-06-28 | 2024-06-28 | Self-adaptive booster oil pump system, hydraulic system, working machine and new energy vehicle |
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| CN118423251B true CN118423251B (en) | 2024-09-24 |
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| JP2000045955A (en) * | 1998-07-31 | 2000-02-15 | Kubota Corp | Hydraulic unit |
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| CN102297248B (en) * | 2011-07-22 | 2013-12-04 | 阮送良 | Automatic centrifugal transmission of electric vehicle |
| CN215444967U (en) * | 2021-02-08 | 2022-01-07 | 博世力士乐（常州）有限公司 | Hydrostatic drive system with freewheel mode |
| CN216447248U (en) * | 2021-10-09 | 2022-05-06 | 中联重科股份有限公司 | Hydraulic system of mixer truck and mixer truck |
| CN117052656A (en) * | 2023-09-21 | 2023-11-14 | 广西柳工机械股份有限公司 | Boosting hydraulic oil tank, gear pump auxiliary oil suction system and engineering machinery |
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| CN201507581U (en) * | 2009-02-21 | 2010-06-16 | 田立中 | Centrifugal clutch |
| CN108331859A (en) * | 2018-01-29 | 2018-07-27 | 安徽展鹏液压机械有限公司 | A kind of Retarder for vehicle retarder brake system |
| CN216666113U (en) * | 2022-01-21 | 2022-06-03 | 安百拓（南京）建筑矿山设备有限公司 | Rotary drill feeding hydraulic system and rotary drill |
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| CN118423251A (en) | 2024-08-02 |
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