CN109372828B - Hydraulic control system for comprehensive transmission device - Google Patents
Hydraulic control system for comprehensive transmission device Download PDFInfo
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- CN109372828B CN109372828B CN201811196019.2A CN201811196019A CN109372828B CN 109372828 B CN109372828 B CN 109372828B CN 201811196019 A CN201811196019 A CN 201811196019A CN 109372828 B CN109372828 B CN 109372828B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
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- C—CHEMISTRY; METALLURGY
- C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
- C22C—ALLOYS
- C22C38/00—Ferrous alloys, e.g. steel alloys
- C22C38/001—Ferrous alloys, e.g. steel alloys containing N
-
- C—CHEMISTRY; METALLURGY
- C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
- C22C—ALLOYS
- C22C38/00—Ferrous alloys, e.g. steel alloys
- C22C38/002—Ferrous alloys, e.g. steel alloys containing In, Mg, or other elements not provided for in one single group C22C38/001 - C22C38/60
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- C—CHEMISTRY; METALLURGY
- C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
- C22C—ALLOYS
- C22C38/00—Ferrous alloys, e.g. steel alloys
- C22C38/02—Ferrous alloys, e.g. steel alloys containing silicon
-
- C—CHEMISTRY; METALLURGY
- C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
- C22C—ALLOYS
- C22C38/00—Ferrous alloys, e.g. steel alloys
- C22C38/04—Ferrous alloys, e.g. steel alloys containing manganese
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- C—CHEMISTRY; METALLURGY
- C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
- C22C—ALLOYS
- C22C38/00—Ferrous alloys, e.g. steel alloys
- C22C38/18—Ferrous alloys, e.g. steel alloys containing chromium
- C22C38/24—Ferrous alloys, e.g. steel alloys containing chromium with vanadium
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- C—CHEMISTRY; METALLURGY
- C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
- C22C—ALLOYS
- C22C38/00—Ferrous alloys, e.g. steel alloys
- C22C38/18—Ferrous alloys, e.g. steel alloys containing chromium
- C22C38/26—Ferrous alloys, e.g. steel alloys containing chromium with niobium or tantalum
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
Abstract
A hydraulic control system for an integrated transmission, comprising: a main oil pump loop, an auxiliary oil pump loop and a control element; the control element is arranged on the main oil pump loop; all the auxiliary oil pump loops are connected to the main oil pump loop through the control element; the control element is configured to: when the vehicle needs to be started at a low temperature, the oil pressure of the main oil pump loop is decompressed, so that the auxiliary oil pump loops are respectively communicated with the main oil pump loop and are unloaded simultaneously; wherein the oil pressure of the main oil pump circuit is greater than the oil pressure of the auxiliary oil pump circuit; the hydraulic control system provided by the invention reduces the pressure of each oil pump when the vehicle is started at low temperature, namely, the starting load of the engine of the special vehicle is reduced, the vehicle does not work at ordinary times, and the respective work of each oil pump does not interfere with each other.
Description
Technical Field
The invention relates to a hydraulic control system, in particular to a hydraulic control system for a comprehensive transmission device.
Background
Starting of a special vehicle engine is difficult in a low-temperature environment, so that the load driven by the engine is required to be smaller and better when the engine is started at a low temperature, and each oil pump of an oil supply system of the comprehensive transmission device is one of the loads to be overcome when the engine is started.
Special vehicles require smooth engine starting at low temperatures, and therefore require a low torque for the low temperature starting of the integrated transmission. In order to reduce the starting torque of the integrated transmission at the low-temperature starting, various schemes can be adopted, such as:
scheme (1) adds heating device, heats positions such as the oil tank of synthesizing transmission before low temperature starts, reduces the viscosity of transmission oil through improving the oil temperature to reduce the rotation of transmission case and stir oil loss, reduce the starting torque. But the proposal needs to add a heating device, has complex structure and consumes energy;
in the scheme (2), before the vehicle is flamed out, the gas pressure of the oil-gas mixed pressure oil tank in the comprehensive transmission device is unloaded to improve the oil liquid height of the pressure oil tank, so that the liquid level height of the oil pan of the transmission case can be reduced. When the transmission case is started, rotating parts such as various gears cannot stir oil, so that the starting torque is reduced. However, the scheme is effective in a short time, but after the vehicle is shut down and parked for a long time, oil in the pressure oil tank slowly leaks to the oil pan due to high oil level until the final liquid level is balanced, and the oil stirring loss is large when the vehicle is started in a cold state;
a solution (3) in which a release mechanism such as a main clutch is used between the engine and the transmission, but the installation space required for this solution is large;
to unload a plurality of oil pumps, a plurality of electromagnetic switch valves can be used for simultaneously electrifying, but the size is too large and the structure is complicated.
Disclosure of Invention
To address the above-discussed deficiencies of the prior art, the present invention provides a hydraulic control system for an integrated transmission.
The technical scheme provided by the invention is as follows: a hydraulic control system for an integrated transmission, comprising: a main oil pump loop, an auxiliary oil pump loop and a control element;
the control element is arranged on the main oil pump loop;
all the auxiliary oil pump loops are connected into the main oil pump loop through the control element;
the control element is configured to: when the vehicle needs to be started at a low temperature, the oil pressure of the main oil pump loop is decompressed, so that the auxiliary oil pump loops are respectively communicated with the main oil pump loop and are unloaded simultaneously;
wherein the oil pressure of the main oil pump circuit is greater than the oil pressure of the sub-oil pump circuit.
Preferably, the control element includes: a normally closed electromagnetic switch valve;
and the inlet of the electromagnetic switch valve is respectively communicated with the main oil pump loop and the auxiliary oil pump loop, and the outlet of the electromagnetic switch valve is communicated with the oil tank.
Preferably, the main oil pump circuit includes: the main oil pump, the pilot overflow constant pressure valve and the damping hole;
the pilot-operated overflow constant pressure valve is a two-stage valve, and comprises: a main valve and a pilot valve;
the main oil pump is respectively communicated with the main valve and the pilot valve;
the damping hole is arranged between the main valve and the pilot valve;
the main valve is used for balancing the pressure difference of the damping hole;
and the pilot valve is communicated with an inlet of the electromagnetic switch valve and is used for setting a constant pressure value of the main oil pump.
Preferably, the method further comprises the following steps: the one-way valves are respectively arranged on each auxiliary oil pump loop;
and each auxiliary oil pump loop is communicated with the main oil pump loop through the one-way valve.
Preferably, the main oil pump circuit further includes: soft and firm springs;
the hard spring is fixedly arranged on the pilot valve and used for setting pilot oil pressure;
the soft spring is fixedly arranged on the main valve and used for setting the opening pressure of the main valve based on the pilot oil pressure and the spring force of the soft spring.
Preferably, each of the sub-oil pump circuits includes: the auxiliary oil pump, the auxiliary valve, the auxiliary pilot valve and the auxiliary damping hole;
the auxiliary oil pump is respectively communicated with the auxiliary valve and the auxiliary pilot valve;
the auxiliary damping hole is arranged between the auxiliary valve and the auxiliary pilot valve;
the auxiliary pilot valve is communicated with the inlet of the electromagnetic switch valve.
Preferably, each of the sub-oil pump circuits further includes: an auxiliary soft spring and an auxiliary hard spring;
the auxiliary hard spring is fixedly arranged on the auxiliary pilot valve;
the auxiliary soft spring is fixedly arranged on the auxiliary valve.
Preferably, a forward oil port of the check valve is communicated with a corresponding auxiliary pilot valve in the auxiliary oil pump loop, and a reverse oil port of the check valve is communicated with a pilot valve in the main oil pump loop.
Preferably, the constant pressure values of the auxiliary oil pumps are different;
and the constant pressure value of each auxiliary oil pump is smaller than that of the main oil pump.
Preferably, the hard spring comprises the following components in percentage by weight: c: 0.50%, Si: 1.50%, Mn: 0.70%, Cr: 0.25%, V: 0.09%, Nb: 0.014%, N: 1.10%, P0.0035%, S0.0035%, and the balance Fe and inevitable impurities.
Compared with the closest prior art, the technical scheme provided by the invention has the following beneficial effects:
(1) the invention provides a hydraulic control system for an integrated transmission, comprising: a main oil pump loop, an auxiliary oil pump loop and a control element; the control element is arranged on the main oil pump loop; all the auxiliary oil pump loops are connected into the main oil pump loop through the control element; the control element is configured to: when the vehicle needs to be started at a low temperature, the oil pressure of the main oil pump loop is decompressed, so that the auxiliary oil pump loops are respectively communicated with the main oil pump loop and are unloaded simultaneously; wherein the oil pressure of the main oil pump circuit is greater than the oil pressure of the auxiliary oil pump circuit; the hydraulic control system provided by the invention reduces the pressure of each oil pump when the vehicle is started at low temperature, namely, the starting load of the engine of the special vehicle is reduced, the vehicle does not work at ordinary times, and the respective work of each oil pump does not interfere with each other.
(2) According to the technical scheme provided by the invention, one electromagnetic switch valve is adopted as a control element, and a plurality of oil pumps are unloaded at the same time, so that the structure is simple and practical, and the load of the engine of the special vehicle can be effectively reduced when the special vehicle is started at a low temperature.
(3) According to the technical scheme provided by the invention, the adopted hard spring can meet the requirements of various harsh working environments, high strength and long service life of the spring, and has excellent delayed fracture resistance, corrosion resistance and fatigue resistance besides high tensile strength.
Drawings
FIG. 1 is a schematic diagram of a hydraulic control system of the present invention;
wherein, P1-main oil pump in main oil pump circuit; PV1 — a pilot valve in the main oil pump loop; RV 1-main valve in main oil pump circuit; j1-orifice in main oil pump circuit; EV-electromagnetic switch valve; p2, P3, and P4 — the secondary oil pump in each secondary oil pump circuit; RV2, RV3 and RV4 — secondary valves in each secondary oil pump circuit; PV2, PV3, and PV4 — secondary pilot valves in each secondary oil pump circuit; p2, P3, and P4 — check valves in each sub oil pump circuit; j2, J3, and J4 — secondary damping orifices in each secondary oil pump circuit.
Detailed Description
For a better understanding of the present invention, the technical solutions of the present invention will be described in further detail below with reference to the accompanying drawings.
As shown in fig. 1, the present invention provides a hydraulic control system for an integrated transmission, including: a main oil pump loop, an auxiliary oil pump loop and a control element;
the control element is arranged on the main oil pump loop;
all the auxiliary oil pump loops are connected to the main oil pump loop through the control element;
the control element is to: when the vehicle needs to be started at a low temperature, the oil pressure of the main oil pump loop is decompressed, so that the auxiliary oil pump loops are respectively communicated with the main oil pump loop and are unloaded simultaneously;
wherein the oil pressure of the main oil pump circuit is greater than the oil pressure of the sub-oil pump circuit.
Preferably, the control element comprises: a normally closed electromagnetic switch valve;
and the inlet of the electromagnetic switch valve is respectively communicated with the main oil pump loop and the auxiliary oil pump loop, and the outlet of the electromagnetic switch valve is communicated with the oil tank.
Preferably, the main oil pump circuit includes: the main oil pump, the pilot overflow constant pressure valve and the damping hole;
the pilot-operated overflow constant pressure valve is a two-stage valve, comprising: a main valve and a pilot valve;
the main oil pump is respectively communicated with the main valve and the pilot valve;
the damping hole is arranged between the main valve and the pilot valve;
the main valve is used for balancing the pressure difference of the damping hole;
and the pilot valve is communicated with an inlet of the electromagnetic switch valve and is used for setting a constant pressure value of the main oil pump.
Preferably, the method further comprises the following steps: the one-way valves are respectively arranged on each auxiliary oil pump loop;
and each auxiliary oil pump loop is communicated with the main oil pump loop through the one-way valve.
Preferably, the main oil pump circuit further includes: soft and firm springs;
the hard spring is fixedly arranged on the pilot valve and used for setting pilot oil pressure;
the soft spring is fixedly arranged on the main valve and used for setting the opening pressure of the main valve based on the pilot oil pressure and the spring force of the soft spring.
Preferably, each of the sub-oil pump circuits includes: the auxiliary oil pump, the auxiliary valve, the auxiliary pilot valve and the auxiliary damping hole;
the auxiliary oil pump is respectively communicated with the auxiliary valve and the auxiliary pilot valve;
the auxiliary damping hole is arranged between the auxiliary valve and the auxiliary pilot valve;
the auxiliary pilot valve is communicated with the inlet of the electromagnetic switch valve.
Preferably, each of the sub-oil pump circuits further includes: an auxiliary soft spring and an auxiliary hard spring;
the auxiliary hard spring is fixedly arranged on the auxiliary pilot valve;
the auxiliary soft spring is fixedly arranged on the auxiliary valve.
Preferably, a forward oil port of the check valve is communicated with a corresponding auxiliary pilot valve in the auxiliary oil pump loop, and a reverse oil port of the check valve is communicated with a pilot valve in the main oil pump loop.
Preferably, the constant pressure value of each auxiliary oil pump is different;
and the constant pressure value of each auxiliary oil pump is smaller than that of the main oil pump.
Preferably, the hard spring comprises the following components in percentage by weight: c: 0.50%, Si: 1.50%, Mn: 0.70%, Cr: 0.25%, V: 0.09%, Nb: 0.014%, N: 1.10%, P0.0035%, S0.0035%, and the balance Fe and inevitable impurities.
Specifically, the starting of the engine of the special vehicle is difficult in a low-temperature environment, so that the load driven by the engine is required to be smaller and better when the engine is started at a low temperature, and each oil pump of the oil supply system of the comprehensive transmission device is one of the loads to be overcome when the engine is started, so that the hydraulic control system provided by the invention can be a hydraulic system for simultaneously unloading each oil supply pump; the pressure of each oil pump is reduced during low-temperature starting, namely the starting load of the engine of the special vehicle is reduced, and the unloading system does not work at ordinary times, and each oil supply pump can still supply oil normally.
The invention adopts the pilot overflow valve as the constant pressure valve of each oil pump, adopts one electromagnetic switch valve as the control element, and connects the pilot oil pressure of each oil pump constant pressure valve in a unified way through a plurality of one-way valves, thus the oil pumps can be unloaded at the same time by controlling the on-off of one electromagnetic switch valve EV, the structure is simple and practical, and the load of the special vehicle engine can be effectively reduced when the vehicle is started at low temperature.
The functional principle is as follows:
the hydraulic control system of the present invention is illustrated in schematic form in FIG. 1 below. The oil supply system of the integrated transmission device of the special vehicle generally adopts a plurality of oil pumps for supplying oil, P1, P2, P3 and P4 are 4 oil pumps of the oil supply system of the integrated transmission device, and each oil pump respectively takes different functions in the integrated transmission device, such as supplying gear shifting oil pressure, supplying converter oil supplement, returning oil from an oil tank and the like, so that the constant pressure value of each oil pump is different, and the maximum constant pressure value of the P1 pump is assumed in the following FIG. 1.
In the hydraulic system, the constant pressure valves of the respective oil pumps are pilot-operated relief valves, and taking the oil path of the P1 pump as an example, the pilot-operated relief constant pressure valve of the P1 pump is a two-stage valve including a pilot stage and a main stage, where RV1 is a main valve, J1 is a damping orifice, and PV1 is a pilot valve. The spring of the PV1 pilot valve sets the pilot oil pressure, which together with the main valve spring force sets the RV1 main valve opening pressure, since the spring of the RV1 main valve only needs to balance the differential pressure of the damping orifice J1 and only receives a small part of the pressure, the flow through the RV1 main valve is large but its spring is soft, while the flow through the pilot valve PV1 is small but its spring is hard. Thus, the flow of the P1 pump oil way overflow mainly overflows through the main valve RV1, and the constant pressure value of the overflow valve is set by the pilot valve PV 1. Similarly, the constant pressure valves of other pumps P2, P3 and P4 have the same principle as the oil circuit of the P1 pump, RV2, RV3 and RV4 are main valves, PV2, PV3 and PV4 are pilot valves, and J2, J3 and J4 are damping holes.
In the hydraulic system, CV2, CV3 and CV4 are check valves, a forward port of each check valve is connected with pilot oil pressure of a constant pressure valve of each of P2, P3 and P4 pumps, a reverse port of each check valve is connected with pilot oil pressure of a constant pressure valve of a P1 pump with the highest pressure value, and therefore the pilot oil pressure of the constant pressure valve of the P1 pump is larger than that of the P2, P3 and P4 pumps when the hydraulic system works, the CV2, CV3 and CV4 check valves are in a closed state at the moment, namely the respective work of oil pump circuits of the P1, P2, P3 and P4 pumps does not interfere with each other.
In the hydraulic system, the EV is a solenoid switch valve, the inlet of the EV is connected to the pilot oil pressure of the P1 pump constant pressure valve, and the outlet of the EV is connected to the oil tank. The EV electromagnetic switch valve is normally closed, is opened when being electrified, and is closed when being powered off.
The main working process is as follows: when the special vehicle needs to be started at a low temperature, the electromagnetic switch valve EV is electrified and opened, so that the pilot oil pressure of the P1 pump constant pressure valve is relieved through the EV, namely the pressure of the PV1 constant pressure port is zero, the pressure of the P1 pump is only set by the soft spring of the RV1, and the pressure of the P1 pump is relieved. Meanwhile, the pilot oil pressure of the P1 pump constant pressure valve is relieved, so that the CV2, CV3 and CV4 one-way valves are all opened, the pilot oil pressure of the P2, P3 and P4 pump constant pressure valves passes through the CV2, CV3 and CV4 one-way valves and is relieved through the EV electromagnetic switch valve, and meanwhile, the pressure of the P2, P3 and P4 pump is relieved. Therefore, 4 oil pumps can be unloaded at the same time by controlling one EV electromagnetic switch valve, the load of cold start of the engine is effectively reduced, after the engine is successfully started, the electromagnetic switch valve EV is powered off, the pressure is respectively built up in the oil pumping circuits of P1, P2, P3 and P4, the pressure value is set by the respective constant pressure valve, the one-way valves of CV2, CV3 and CV4 are in a closed state, and the set pressures of the oil pumping circuits do not interfere with one another.
In the schematic diagram of the hydraulic control system of fig. 1, only 4 sets of oil pumps are shown, and in fact, more oil pump circuits can be unloaded simultaneously by adopting the same principle.
The present invention is not limited to the above embodiments, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention are included in the scope of the claims of the present invention which are filed as the application.
Claims (2)
1. A hydraulic control system for an integrated transmission, comprising: a main oil pump loop, an auxiliary oil pump loop and a control element;
the control element is arranged on the main oil pump loop;
all the auxiliary oil pump loops are connected to the main oil pump loop through the control element;
the control element is to: when the vehicle needs to be started at a low temperature, the oil pressure of the main oil pump loop is decompressed, so that the auxiliary oil pump loops are respectively communicated with the main oil pump loop and are unloaded simultaneously;
wherein the oil pressure of the main oil pump circuit is greater than the oil pressure of the auxiliary oil pump circuit;
the control element includes: a normally closed electromagnetic switch valve;
an inlet of the electromagnetic switch valve is communicated with the main oil pump loop and the auxiliary oil pump loop respectively, and an outlet of the electromagnetic switch valve is communicated with an oil tank;
the main oil pump circuit includes: the main oil pump, the pilot overflow constant pressure valve and the damping hole;
the pilot-operated overflow constant pressure valve is a two-stage valve, and comprises: a main valve and a pilot valve;
the main oil pump is respectively communicated with the main valve and the pilot valve;
the damping hole is arranged between the main valve and the pilot valve;
the main valve is used for balancing the pressure difference of the damping hole;
the pilot valve is communicated with an inlet of the electromagnetic switch valve and is used for setting a constant pressure value of the main oil pump;
further comprising: the one-way valves are respectively arranged on each auxiliary oil pump loop;
each auxiliary oil pump loop is communicated with the main oil pump loop through the one-way valve;
the main oil pump loop further comprises: soft and firm springs;
the hard spring is fixedly arranged on the pilot valve and used for setting pilot oil pressure;
the soft spring is fixedly arranged on the main valve and used for setting the opening pressure of the main valve based on the pilot oil pressure and the spring force of the soft spring;
each of the sub-oil pump circuits includes: the auxiliary oil pump, the auxiliary valve, the auxiliary pilot valve and the auxiliary damping hole;
the auxiliary oil pump is respectively communicated with the auxiliary valve and the auxiliary pilot valve;
the auxiliary damping hole is arranged between the auxiliary valve and the auxiliary pilot valve;
the auxiliary pilot valve is communicated with an inlet of the electromagnetic switch valve;
each of the sub-oil pump circuits further includes: an auxiliary soft spring and an auxiliary hard spring;
the auxiliary hard spring is fixedly arranged on the auxiliary pilot valve;
the auxiliary soft spring is fixedly arranged on the auxiliary valve;
a forward oil port of the one-way valve is communicated with a corresponding auxiliary pilot valve in the auxiliary oil pump loop, and a reverse oil port of the one-way valve is communicated with a pilot valve in the main oil pump loop;
the constant pressure values of the auxiliary oil pumps are different;
and the constant pressure value of each auxiliary oil pump is smaller than that of the main oil pump.
2. The hydraulic control system of claim 1,
the hard spring is prepared from the following components in percentage by weight: c: 0.50%, Si: 1.50%, Mn: 0.70%, Cr: 0.25%, V: 0.09%, Nb: 0.014%, N: 1.10%, P0.0035%, S0.0035%, and the balance Fe and inevitable impurities.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811196019.2A CN109372828B (en) | 2018-10-15 | 2018-10-15 | Hydraulic control system for comprehensive transmission device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811196019.2A CN109372828B (en) | 2018-10-15 | 2018-10-15 | Hydraulic control system for comprehensive transmission device |
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| CN109372828A CN109372828A (en) | 2019-02-22 |
| CN109372828B true CN109372828B (en) | 2022-09-09 |
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| CN110789507B (en) * | 2019-11-05 | 2021-06-22 | 南京经纬达汽车科技有限公司 | Independent booster pump distributed autonomous braking system with shaft pressure equalization |
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| CN107630839A (en) * | 2017-10-25 | 2018-01-26 | 北京富力通达科技有限公司 | A kind of hydraulic pressure soft starting device and its application method |
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