CN115076022A - Core of hydraulic vane motor, hydraulic vane motor and hydraulic transmission system - Google Patents
Core of hydraulic vane motor, hydraulic vane motor and hydraulic transmission system Download PDFInfo
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- CN115076022A CN115076022A CN202110257792.0A CN202110257792A CN115076022A CN 115076022 A CN115076022 A CN 115076022A CN 202110257792 A CN202110257792 A CN 202110257792A CN 115076022 A CN115076022 A CN 115076022A
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 29
- 239000007788 liquid Substances 0.000 claims abstract description 431
- 238000009826 distribution Methods 0.000 claims abstract description 336
- 238000012937 correction Methods 0.000 claims abstract description 47
- 238000000034 method Methods 0.000 claims abstract description 44
- 230000008569 process Effects 0.000 claims abstract description 40
- 239000012530 fluid Substances 0.000 claims description 91
- 238000002347 injection Methods 0.000 claims description 87
- 239000007924 injection Substances 0.000 claims description 87
- 230000033001 locomotion Effects 0.000 claims description 42
- 238000004891 communication Methods 0.000 claims description 30
- 238000006073 displacement reaction Methods 0.000 claims description 27
- 230000009471 action Effects 0.000 claims description 18
- 230000001105 regulatory effect Effects 0.000 claims description 12
- 230000008859 change Effects 0.000 claims description 9
- 238000007599 discharging Methods 0.000 claims description 6
- 230000003247 decreasing effect Effects 0.000 claims description 4
- 230000007246 mechanism Effects 0.000 claims description 4
- 230000009467 reduction Effects 0.000 claims description 2
- 230000000149 penetrating effect Effects 0.000 claims 2
- 230000008602 contraction Effects 0.000 description 8
- 230000006872 improvement Effects 0.000 description 7
- 230000007547 defect Effects 0.000 description 6
- 239000000243 solution Substances 0.000 description 6
- 238000005299 abrasion Methods 0.000 description 4
- 230000001360 synchronised effect Effects 0.000 description 4
- 238000011038 discontinuous diafiltration by volume reduction Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 230000010349 pulsation Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 238000004134 energy conservation Methods 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C2/00—Rotary-piston engines
- F03C2/30—Rotary-piston engines having the characteristics covered by two or more of groups F03C2/02, F03C2/08, F03C2/22, F03C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F03C2/304—Rotary-piston engines having the characteristics covered by two or more of groups F03C2/02, F03C2/08, F03C2/22, F03C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movements defined in sub-group F03C2/08 or F03C2/22 and relative reciprocation between members
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- Engineering & Computer Science (AREA)
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- General Engineering & Computer Science (AREA)
- Hydraulic Motors (AREA)
Abstract
The invention relates to the technical field of hydraulic transmission, and discloses a vane motor core which comprises: a groove bottom cavity balance liquid distribution channel is arranged between the middle part between two correction angles at the head part of the blade and the groove bottom cavity corresponding to the blade in the rotating part, and a groove bottom cavity intermittent liquid distribution channel which determines whether the front and rear side working cavities of the blade are respectively communicated with the corresponding groove bottom cavity or not is arranged between the front and rear side working cavities corresponding to the blade and the corresponding groove bottom cavity in the rotating part according to the circumferential position of the blade; during operation, the tank bottom cavity balance liquid distribution channel is matched with the cavity intermittent liquid distribution channel to ensure that the tank bottom cavity obtains sectional optimized liquid distribution, so that the contact working condition of the blade head and the inner surface of the stator generated by hydraulic force is improved; the invention also discloses a hydraulic primary-secondary blade motor with the core and a hydraulic transmission system with the motor; the motor improves the working pressure, has reliable performance and can be produced by utilizing the prior process and equipment.
Description
Technical Field
The invention belongs to the technical field of hydraulic transmission, and particularly relates to a core of a hydraulic vane motor, the hydraulic vane motor with the core and a hydraulic transmission system with the hydraulic vane motor.
Background
In order to ensure the normal operation of the hydraulic vane motor, the heads (correction angles) of the vanes in the movement must be always in contact with the inner surface of the stator in the movement in the whole operation process of the motor.
To improve the working pressure of the hydraulic vane motor, the problem that the inner surface of a stator fails due to abrasion because the contact stress between the head (correction angle) of a vane in a movement and the inner surface of the stator in the movement is overlarge is firstly solved.
The vane motor has a structure similar to that of a vane pump, and the vane structure channels of the vane motor are generally of a single-vane type, a double-vane type, a combined-vane type, a spring vane type, a pin vane type, a double-stage vane type and the like.
The text in the above two citations is taken from the handbook of hydropneumatic technology, published by the mechanical industry publishers, p 551.
The blade structure of the existing hydraulic primary-secondary blade motor is explained in the following way in comparison with the blade structure of the existing hydraulic primary-secondary blade pump:
the existing hydraulic primary and secondary vane pump is characterized in that the lower parts of all vanes (in a primary and secondary vane motor core) are manufactured into ' primary and secondary ' vanes (a primary vane and a secondary vane) with separated middles in a ' primary and secondary vane mode, the head of the primary vane is divided into a front part and a rear part by a contact line of the head of the primary vane and the inner surface of a stator, and oil (working liquid) in a working volume (a working cavity) adjacent to the part with larger radial area of the head of the primary vane is introduced into the bottom (the cavity) of the vane slot in a rotor. The closed small chamber (blade middle chamber) in the middle of the primary and secondary blades is always connected with an oil discharge chamber (inlet pressure working fluid of the existing hydraulic primary and secondary blade motor). In the oil suction area (the common liquid outlet section of the extended outlet area where the working chambers at the front side and the rear side of the female blade in the existing hydraulic primary-secondary blade motor are simultaneously connected), the hydraulic pressure extending outwards of the female blade is only generated by the pressure of the oil discharge (the inlet pressure working liquid of the hydraulic primary-secondary blade motor) acting on the middle part (the blade middle chamber) of the female blade, so that the contact stress between the outer end (head) of the female blade and the slide way (the inner surface of the stator) is reduced. The method has no special difficulty in the aspect of manufacturing technology, and is widely applied. "
The contents of the citation, except for the text in parentheses, are taken from the handbook of hydropneumatic technology, published by mechanical industry publishers, page 484.
The core working pressure of the existing hydraulic primary-secondary blade type hydraulic motor is feasible in a certain range, if the working pressure needs to be further improved, the radial effective area set by the blade middle cavity cannot be changed, so that the middle cavity liquid distribution channel structure enables the contact stress of the head of a working female blade in the common liquid outlet section and the inner surface of a stator to be synchronously improved, a fluid film layer is penetrated to cause unreliable work, the abrasion and the working performance of the stator are deteriorated, two working cavities corresponding to the same blade and having unequal adjacent volumes are simultaneously connected and extend to an injection port, a rotor of the hydraulic blade motor rotates towards the direction of the working cavity with a relatively larger volume in work, the head of the female blade in the common liquid inlet section of the hydraulic blade pump is a stator inner surface expanding section, and the head of the female blade in the common liquid outlet section of the hydraulic blade motor is a stator inner surface contracting section, the friction between the head of the female blade of the hydraulic blade motor and the inner surface of the stator is more violent, so that the working pressure of the hydraulic blade motor is lower, and the defect existing in the movement needs to be further improved; the movement adopted by the existing hydraulic master-slave blade type hydraulic motor limits the further improvement of the working pressure of the motor, and needs to be further improved aiming at the defects of the existing hydraulic master-slave blade type hydraulic motor.
The hydraulic transmission system adopting the existing hydraulic master-slave blade type hydraulic motor has the unique advantages of small flow pulsation, lower noise and large power-mass ratio, but is limited by the working pressure of the existing hydraulic master-slave blade type hydraulic motor, so that the working pressure of the hydraulic transmission system cannot be further improved.
In order to lead the hydraulic transmission system to adapt to the continuous development towards high pressure, energy conservation, high efficiency and environmental protection, and adapt to the use of low-viscosity fluid or high-water-based working medium, the defects of the hydraulic transmission system need to be further improved.
Disclosure of Invention
As mentioned above, further improvements have been made to the prior art, and in particular to the core of the master-slave blade motor, the hydraulic master-slave blade motor, and the hydraulic transmission system using the existing hydraulic master-slave blade motor, which have certain drawbacks.
The first technical problem to be solved by the invention is to solve the defect of a liquid distribution structure of a blade slot bottom cavity in a core of a hydraulic primary-secondary blade type motor, in order to enable each slot bottom cavity in the core to be capable of being configured with working liquid with sectional optimized pressure in an action period, and to enable contact stress of a blade head correction angle and the inner surface of a stator of each section to be adjusted and improved, so that the core can still maintain normal operation at higher working pressure.
The second technical problem to be solved by the invention is to overcome the defects of the existing hydraulic master-slave blade motor adopting the original core, so as to achieve the purpose of improving the working pressure of the hydraulic blade motor.
The third technical problem to be solved by the invention is to solve the defects of the hydraulic transmission system adopting the existing hydraulic master-slave blade motor so as to achieve the purpose of improving the working pressure of the hydraulic transmission system.
In order to solve the first technical problem, the present invention provides a movement of a hydraulic vane motor, and the purpose of the present invention is achieved by the following technical solutions:
a cartridge for a hydraulic vane motor, comprising: the rotor comprises a stator, a rotor, blades, a left end cover and a right end cover; the surface of the inner cavity of the stator comprises one group or a plurality of groups of two variable-diameter sections which are circumferentially changed from the axis of the movement and are not connected with each other, the rotor is provided with a plurality of rotor blade grooves and can be rotatably arranged in the inner cavity of the stator, the blades can be telescopically arranged in each rotor blade groove, a spring which enables a mother blade to have the outward radial stretching tendency is arranged between each blade and the rotor, and the left end cover and the right end cover are respectively positioned at two axial ends of the stator; the rotor and the blades mainly form a rotating part in the machine core;
a working cavity is correspondingly formed between two adjacent and extended blades, the rotor, the stator and the two end covers; a groove bottom cavity is correspondingly formed among the blade, the rotor blade groove and the two end covers;
the core of the hydraulic vane motor is arranged in the inner cavity of the motor shell with an injection port for injecting high-pressure working fluid and a discharge port for discharging low-pressure working fluid; the core of the hydraulic vane motor comprises an extension filling opening and an extension discharging opening: the injection port can be communicated with the working cavity in contact with one of the reducing sections by adopting an extension injection port, the discharge port can be communicated with the working cavity in contact with the other reducing section by adopting an extension discharge port, and the extension injection port and the extension discharge port are circumferentially arranged in a separated manner and cannot be communicated with the same working cavity at the same time; the diameter-changing section of the inner surface of the stator corresponding to the extension injection port is an expanding section, and the diameter-changing section corresponding to the extension discharge port is a reducing section;
the core of the hydraulic vane motor is a mechanism for converting pressure energy of high-pressure working fluid in a working cavity communicated with the extending injection port into mechanical energy for driving the rotor to rotate, two adjacent working cavities corresponding to the same vane are simultaneously positioned in the working of the diameter expanding section, and the rotor rotates towards the working cavity with larger volume; a transmission shaft penetrates through the core of the hydraulic vane motor, and a rotor in the core drives the transmission shaft to work;
the volume of the working cavity is periodically and correspondingly changed along with the radial displacement of the corresponding blade in the rotary displacement, the working cavity which is communicated with the extension injection port and is in contact with the diameter expansion section of the surface of the inner surface of the stator is injected into the working cavity by high-pressure working liquid when the volume is increased, and the working cavity which is communicated with the extension discharge port and is in contact with the diameter reduction section of the surface of the inner surface of the stator is discharged out of the working cavity when the volume is decreased; so that the working fluid pressure in each working chamber has the characteristic of section-wise change;
the method is characterized in that:
the head of the blade is at least provided with a front correction angle and a rear correction angle which can simultaneously contact the inner surface of the stator in the direction corresponding to the rotation direction of the rotor, and the middle part of the head of the blade is formed between the top ends of the front correction angle and the rear correction angle;
a tank bottom cavity balance liquid distribution channel is arranged in the rotating part and is used for enabling the corresponding tank bottom cavity where the blade is located to be communicated with the middle part of the head of the blade all the time;
in the working period, when a side correcting angle of the extending blade is separated from the inner surface of the stator, the side clearance channel is formed between the side working cavity adjacent to the side correcting angle in the blade and the middle part of the blade head of the blade; in the process that the volumes of the front working cavity and the rear working cavity are simultaneously increased, the corresponding tank bottom cavity is communicated with the front working cavity through the corresponding balance liquid distribution channel, the middle part of the blade head and the front clearance channel;
the rotary part is provided with a groove bottom cavity intermittent liquid distribution channel which is used for enabling the groove bottom cavity corresponding to the blade to be intermittently communicated with the front side working cavity and the rear side working cavity;
in the working process that at least the volumes of the working cavities on the front side and the rear side of the blade are increased at the same time, the corresponding tank bottom cavity is switched from the working cavity communicated with the front side through the tank bottom cavity intermittent liquid distribution channel to the working cavity communicated with the rear side through the tank bottom cavity intermittent liquid distribution channel, and at least in the working process that the volumes of the working cavities on the front side and the rear side of the blade are decreased at the same time, the corresponding tank bottom cavity is switched from the working cavity communicated with the rear side through the tank bottom cavity intermittent liquid distribution channel to the working cavity communicated with the front side through the tank bottom cavity intermittent liquid distribution channel;
each tank bottom cavity is provided with a corresponding tank bottom cavity auxiliary liquid distribution channel and a corresponding tank bottom cavity intermittent liquid distribution channel;
in the action period work, the bottom cavities of the grooves can obtain segmental change of the working fluid pressure in the respective cavities from the correspondingly communicated working cavities under the mutual matching of the corresponding clearance channels, the bottom cavity balance fluid distribution channels and the bottom cavity intermittent fluid distribution channels, so that the contact stress formed by the hydraulic force of the head parts of the blades and the inner surface of the stator of the extension injection inlet section is adjusted and improved.
In the alternate switching and the re-switching of the intermittent liquid distribution channels of the tank bottom cavities, when the intermittent liquid distribution channels of the tank bottom cavities can not enable the corresponding tank bottom cavities to be communicated with the working cavities, the corresponding tank bottom cavities can be communicated with at least one side working cavity through the balanced liquid distribution channels of the tank bottom cavities.
Preferably, the blade is designed in such a way that the rear part of the blade head, which is divided by an axial contact line between the rear correction angle of the blade and the inner surface of the stator aiming at the extension discharge port, is contacted with low-pressure working fluid, and the rest part of the blade head and the tail part of the blade are contacted with high-pressure working fluid by the extension filling port and the groove bottom cavity balance fluid distribution channel, according to the hydraulic force which is required by the blade to keep the extension trend to the outer diameter and tends to the outer diameter, the radial area of the rear part of the blade head is correspondingly designed; the radial area of the front part of the blade head is correspondingly designed according to the hydraulic force which is required to lead the blade to keep the outward diameter expansion trend and tends to the outward diameter.
In the scheme, the tank bottom cavity intermittent liquid distribution channel is divided into a first type tank bottom cavity intermittent liquid distribution channel and a second type tank bottom cavity intermittent liquid distribution channel: the first type of groove bottom cavity intermittent liquid distribution channel is arranged between the rear side working cavity and the corresponding groove bottom cavity and is used for enabling the corresponding groove bottom cavity to be intermittently communicated with the rear side working cavity during working, and the second type of groove bottom cavity intermittent liquid distribution channel is arranged between the front side working cavity and the corresponding groove bottom cavity and is used for enabling the corresponding groove bottom cavity to be intermittently communicated with the front side working cavity during working;
the blade is positioned on the circumferential position of the inner surface of the stator, the respective volume sizes of the front and rear side working cavities of the blade are controlled, in an action period, the first type of tank bottom cavity intermittent liquid distribution channel enables the rear side working cavity with relatively large volume and maximum volume to be communicated with the corresponding tank bottom cavity, and the second type of tank bottom cavity intermittent liquid distribution channel enables the front side working cavity with relatively small volume and minimum volume to be communicated with the corresponding tank bottom cavity; the first type of tank bottom cavity intermittent liquid distribution channel enables the communication working condition of the rear side working cavity and the corresponding tank bottom cavity to be alternately switched and then switched with the communication working condition of the second type of tank bottom cavity intermittent liquid distribution channel enables the front side working cavity and the corresponding tank bottom cavity to be switched in one of the following three modes:
the first mode is as follows: the switching is arranged in the process that the working cavities on the front side and the rear side are simultaneously enlarged, when the corresponding tank bottom cavity is communicated with the rear working cavity which is connected with the extending injection port and has the enlarged volume through the first-class tank bottom cavity intermittent liquid distribution channel, the switching is started, when the corresponding groove bottom cavity is communicated with the front side working cavity which is connected with the extension injection port and has larger volume through the second type groove bottom cavity intermittent liquid distribution channel, the switching is completed, the re-switching can be arranged in the process from the rear side working and separating from the extension injection port to the front side working cavity communicated with the extension injection port, when the corresponding tank bottom cavity is communicated with the front side working cavity which is connected with the extension outlet and has a reduced volume through the second type of tank bottom cavity intermittent liquid distribution channel, the switching is started again, when the corresponding tank bottom cavity is communicated with the rear side working cavity which is connected with the extension discharge port and has a reduced volume through the first type of tank bottom cavity intermittent liquid distribution channel, the switching is completed;
the second way is: the switching is at least arranged in the process that the front side working cavity and the rear side working cavity are simultaneously enlarged, the switching is started when the corresponding tank bottom cavity is communicated with the front side working cavity which is connected with the extension injection port through the second type tank bottom cavity intermittent liquid distribution channel and the volume of which is enlarged, the switching is completed when the corresponding tank bottom cavity starts to be communicated with the rear side working cavity which is connected with the extension injection port through the first type tank bottom cavity intermittent liquid distribution channel and the volume of which is enlarged, the switching is arranged in the process that the front side working cavity and the rear side working cavity are simultaneously reduced, the switching is started when the corresponding tank bottom cavity is communicated with the rear side working cavity which is connected with the extension discharge port through the first type tank bottom cavity intermittent liquid distribution channel and the volume of which is reduced, and the switching is completed when the corresponding tank bottom cavity starts to be communicated with the front side working cavity which is connected with the extension discharge port through the second type tank bottom cavity intermittent liquid distribution channel and the volume of which is reduced;
or the third mode is as follows: the switching is at least arranged in the process that the working cavities on the front side and the rear side are simultaneously enlarged, when the corresponding tank bottom cavity is communicated with the front side working cavity which is connected with the extension injection port and has enlarged volume through the second type of tank bottom cavity intermittent liquid distribution channel, the switching is started, when the corresponding groove bottom cavity is communicated with the rear side working cavity which is connected with the extending injection port and has a larger volume through the first type groove bottom cavity intermittent liquid distribution channel, the switching is completed, the re-switching can be arranged in the process from the rear side working and separating from the extension injection port to the front side working cavity communicated with the extension injection port, when the corresponding tank bottom cavity is communicated with the front side working cavity which is connected with the extension outlet and has a reduced volume through the second type of tank bottom cavity intermittent liquid distribution channel, the switching is started again, when the corresponding tank bottom cavity is communicated with the rear side working cavity which is connected with the extension discharge port and has a reduced volume through the first type tank bottom cavity intermittent liquid distribution channel, the switching is completed.
As a further improvement, the rotor blade grooves are provided with selected radial inclination angles corresponding to the rotation direction of the rotor within the range of 0-5 degrees; when the inclination angle of the rotor blade slot is such that the middle part of the blade head of the blade on the corresponding slot bottom cavity has a process of communicating the same extension injection port through the front side clearance channel and the front side working cavity and then through the rear side clearance channel and the rear side working cavity, the second mode adopted for the alternating switching and the switching again can be set in the process, or the third mode adopted for the alternating switching and the switching again can be set. The inner surface of the stator is contacted by at least a rear correction angle when the vane is at the maximum radial position and by at least a front correction angle when the vane is at the minimum radial position, thereby reducing the inner leakage of the pump.
Preferably, the first-type tank bottom cavity intermittent liquid distribution channel is arranged in a corresponding part of a blade at the front side of the rear side working cavity, and the communication and disconnection between the corresponding tank bottom cavity and the rear side working cavity are regulated and controlled by the radial displacement of the blade; or the first groove bottom cavity intermittent liquid distribution channel part is arranged in a corresponding part of the blade with a contact surface with the rear side working cavity, and the first groove bottom cavity intermittent liquid distribution channel part is partially arranged in a corresponding part of the rotor and can be mutually matched and communicated, and the communication and disconnection between the corresponding groove bottom cavity and the rear side working cavity are regulated and controlled by the radial displacement of the corresponding blade;
the intermittent liquid distribution of the second groove bottom cavity is arranged in the corresponding part of the rear blade of the front side working cavity, and the communication and disconnection between the corresponding groove bottom cavity and the front side working cavity are regulated and controlled by the radial displacement of the blade; or the intermittent liquid distribution channel part of the groove bottom cavity of the second type is arranged in a corresponding part of the blade with a contact surface with the front side working cavity, and the intermittent liquid distribution channel part is partially arranged in a corresponding part of the rotor and can be mutually matched and communicated, and the communication and disconnection between the corresponding groove bottom cavity and the front side working cavity are regulated and controlled by the radial displacement of the corresponding blade;
and intermittent liquid distribution channels of a first type and a second type of groove bottom cavities adopting a third switching and re-switching mode are respectively arranged in corresponding parts of at least two blades and corresponding parts of the rotor.
Therefore, the intermittent liquid distribution channel of the tank bottom cavity enables the corresponding blade to become a valve core of the two-position three-way reversing valve, and the liquid distribution structure for enabling the corresponding tank bottom cavity to obtain sectional adjustment working liquid pressure in the working process is simplified.
The first end of the tank bottom cavity balance liquid distribution channel penetrates through the middle part of the head of the blade, and the second end of the tank bottom cavity balance liquid distribution channel penetrates through the tail of the blade and is communicated with the corresponding tank bottom cavity; or the first end of the tank bottom cavity balance liquid distribution channel penetrates through the middle part of the head part of the blade, and the second end of the tank bottom cavity balance liquid distribution channel penetrates through the side wall of the blade and can be communicated with the corresponding tank bottom cavity through the groove in the rotor all the time. The working fluid pressure in the middle part of the blade head and the corresponding groove bottom cavity is kept balanced relatively.
The middle part of the blade head is provided with a groove which can form the penetration of the middle part of the blade head by the first end in the corresponding groove bottom cavity balance liquid distribution channel; in order to ensure that the working fluid in the middle part of the blade head is axially and correspondingly unblocked.
As a further improvement, the extended injection ports are provided in the left and right end caps and/or the stator; the extended drain is disposed in at least one end cap and/or stator; thus, the sectional area of the liquid distribution channel of the working cavity is ensured, and the liquid distribution flow rate of the working cavity is controlled.
As an improvement, the stator is provided with a liquid inlet matching channel corresponding to the middle part of the head of the blade in the range that the front side working cavity and the rear side working cavity are simultaneously communicated with the extending injection port and/or a liquid outlet matching channel corresponding to the middle part of the head of the blade in the range that the front side working cavity and the rear side working cavity are simultaneously communicated with the extending discharge port, so that the sectional area of the balanced liquid distribution channel of the bottom cavity of the groove is fully utilized in the working process.
As an improvement, a liquid inlet direct connection channel which enables the liquid inlet matching channel to become an extension filling opening or/and a liquid outlet direct connection channel which enables the liquid outlet matching channel to become an extension discharging opening are/is arranged in the stator, so that the motor enables the working cavity to obtain reasonable liquid distribution flow speed in the volume change process at higher rotating speed.
The core of the hydraulic vane motor adopting the improved tank bottom cavity liquid distribution structure cancels an annular liquid distribution channel which is arranged on the plane of an end cover and is always connected with an extension injection port in the core of the existing master-slave vane motor, and the core completely or partially eliminates the internal leakage increased by an annular groove in the end cover in the motion gap between the axial two end surfaces of a rotor and a vane and the corresponding planes of the two end covers in the working process, thereby basically solving the other problem that the internal leakage in the core in the working process needs to be reduced in the problem of further improving the working pressure proposed by the hydraulic industry; the movement of the hydraulic vane motor adopting the improved tank bottom cavity liquid distribution structure provides technical support for further improving the working pressure of the motor.
In order to solve the second technical problem, the present invention provides a hydraulic vane motor, and the object of the present invention is achieved by the following technical solutions:
the hydraulic vane motor is provided with the movement.
In the hydraulic vane motor adopting the movement of the hydraulic vane motor, inlet pressure working fluid is introduced from the outside of the motor through the groove bottom cavity intermittent fluid distribution channel, the front side working cavity and/or the rear side working cavity connected with the extension injection port, the extension injection port and the injection port when the volume of the groove bottom cavity is increased; the tank bottom cavity discharges the outlet pressure working fluid out of the motor through the tank bottom cavity intermittent fluid distribution channel, the corresponding front side working cavity and/or rear side working cavity connected with the extension discharge port, the extension discharge port and the discharge port when the volume of the tank bottom cavity is reduced; the flow of the working fluid generated by the tank bottom cavity in the volume change is totally summarized to the geometric displacement of the hydraulic vane motor, so that the volume efficiency and the total working efficiency of the improved hydraulic vane motor are improved, and the flow pulsation and the working noise are reduced.
In order to solve the third technical problem, the present invention provides a hydraulic transmission system, and the purpose of the present invention is achieved by the following technical solutions:
a hydraulic drive system includes an actuator; as an improvement: the actuator is internally provided with the hydraulic vane motor.
When the hydraulic transmission system comprises a power source internally provided with the hydraulic vane motor, the hydraulic transmission system still can utilize the hydraulic vane motor to have the unique advantages of smaller flow pulsation, lower noise and large power-mass ratio, and the working pressure of the hydraulic transmission system is further improved; the hydraulic transmission system can meet the development requirements of high pressure, energy conservation, high efficiency and environmental protection, and is more suitable for adopting low-viscosity fluid or high-water-based working medium.
The hydraulic vane motor with the improved tank bottom cavity liquid distribution structure is reasonable in structure and can be produced by utilizing the existing processing equipment and manufacturing process.
Drawings
Fig. 1 is a cross-sectional view of a double acting hydraulic vane motor in embodiment 1 of the present invention;
figure 2 is a cross-sectional view of a movement in embodiment 1 of the present invention;
fig. 3 is an exploded view of the structure of the movement in embodiment 1 of the present invention;
FIG. 4 is a schematic structural view of a left end cap in embodiment 1 of the present invention;
FIG. 5 is a cross-sectional view taken along line A-A of FIG. 4;
FIG. 6 is a schematic structural view of another perspective of the left end cap in embodiment 1 of the present invention;
FIG. 7 is a schematic view of the structure of a stator in embodiment 1 of the present invention
FIG. 8 is a cross-sectional view taken along line A-A of FIG. 7;
FIG. 9 is a schematic view of another view of the stator structure in embodiment 1 of the present invention
FIG. 10 is a schematic structural view of a right end cap in embodiment 1 of the present invention;
FIG. 11 is a cross-sectional view taken along line A-A of FIG. 10;
FIG. 12 is a schematic structural diagram of a right end cap according to another view in embodiment 1 of the present invention;
FIG. 13 is a schematic structural view of a rotor in embodiment 1 of the invention;
FIG. 14 is a cross-sectional view taken along line A-A of FIG. 13;
FIG. 15 is a schematic structural view of the rotor in accordance with another aspect of embodiment 1 of the present invention;
FIG. 16 is a schematic view of the structure of a blade in embodiment 1 of the invention;
FIG. 17 is a schematic view of another perspective of the blade in embodiment 1 of the present invention;
FIG. 18 is a schematic structural view of a blade in example 1 of the present invention from a further perspective;
FIG. 19 is a cross-sectional view taken along line A-A of FIG. 17;
FIG. 20 is a schematic structural view of a further perspective of a blade in accordance with embodiment 1 of the present invention;
FIG. 21 is a schematic view showing the main solution preparation route of the tank bottom chamber in example 1 of the present invention;
FIG. 22 is a schematic view of the main dispensing path of the tank bottom chamber at a different circumferential position than that of FIG. 21;
FIG. 23 is an enlarged view of I of FIG. 21;
figure 24 is a cross-sectional view of a cartridge in accordance with embodiment 8 of the present invention;
FIG. 25 is a schematic view of a left end cap in embodiment 8 of the present invention;
FIG. 26 is a sectional view taken along line A-A of FIG. 25;
fig. 27 is a schematic structural view of a stator in embodiment 8 of the invention;
FIG. 28 is a cross-sectional view taken along line A-A of FIG. 27;
FIG. 29 is a schematic structural view of a right end cap in embodiment 8 of the present invention;
FIG. 30 is a cross-sectional view taken along line A-A of FIG. 29;
FIG. 31 is a schematic view showing the structure of a blade in embodiment 8 of the invention;
FIG. 32 is a schematic structural view of a blade in another perspective according to embodiment 8 of the present invention;
FIG. 33 is a schematic structural view of a blade in accordance with embodiment 8 of the present invention;
FIG. 34 is a cross-sectional view taken along line A-A of FIG. 32;
FIG. 35 is a cross-sectional view taken along line B-B of FIG. 32;
FIG. 36 is a schematic structural view of a rotor in embodiment 8 of the invention;
FIG. 37 is a sectional view taken along line A-A of FIG. 36;
FIG. 38 is a schematic view showing the main solution distribution route of the tank bottom chamber in example 8 of the present invention;
FIG. 39 is a schematic view of the main dispensing path of the tank bottom chamber at a different circumferential position than that of FIG. 38;
FIG. 40 is an enlarged view of I of FIG. 38;
FIG. 41 is a schematic view of a left end cap in embodiment 9 of the present invention;
FIG. 42 is a sectional view taken along line A-A of FIG. 41;
fig. 43 is a sectional view of a stator in embodiment 9 of the invention;
FIG. 44 is a cross-sectional view taken along line A-A of FIG. 43;
FIG. 45 is a schematic structural view of a right end cap in embodiment 9 of the present invention;
FIG. 46 is a sectional view taken along line A-A of FIG. 45;
FIG. 47 is a schematic view of a structure of a blade in embodiment 9 of the invention;
FIG. 48 is a schematic view of a blade in accordance with embodiment 9 of the present invention;
FIG. 49 is a schematic structural view of a blade in accordance with example 9 of the present invention;
FIG. 50 is a cross-sectional view taken along line A-A of FIG. 48;
FIG. 51 is a cross-sectional view taken along line B-B of FIG. 48;
fig. 52 is a sectional view of a rotor in embodiment 9 of the invention;
FIG. 53 is a cross-sectional view taken along line A-A of FIG. 52;
FIG. 54 is a schematic view showing the main solution distribution route of the tank bottom chamber in example 9 of the present invention;
FIG. 55 is a schematic view of the main dispensing path of the tank bottom chamber at a different circumferential position than that of FIG. 54;
FIG. 56 is an enlarged view of section I of FIG. 55;
FIG. 57 is an enlarged view of section II of FIG. 54;
FIG. 58 is an enlarged view of section IV of FIG. 57;
FIG. 59 is an enlarged view of section III of FIG. 54;
FIG. 60 is an enlarged view of the V portion of FIG. 59;
fig. 61 is a sectional view of a double acting through-shaft multiple hydraulic vane motor in embodiment 10 of the present invention.
Detailed Description
The invention is described in further detail below with reference to the accompanying examples.
This application is equipped with the hydraulic vane motor of above-mentioned core, and the tank bottom chamber in this hydraulic vane motor's structure makes the work pour into high-pressure working fluid into from the motor in the volume diminishes outside, and the tank bottom chamber is let out the motor with low pressure working fluid in the volume diminishes outside.
The hydraulic traditional system provided with the hydraulic vane motor has the same position and arrangement mode as the hydraulic traditional system in the hydraulic transmission system.
The embodiments of the present application mainly explain the overall structure of the hydraulic vane motor, and the preferred modes for implementing the present invention will be further described with reference to the accompanying drawings, and the present invention is not limited by the features of the drawings and the preferred embodiments.
Example 1: the present embodiment is a double-acting hydraulic vane motor, which mainly includes, as shown in fig. 1 to 23: the device comprises a left machine shell 1-1, a stator 2, a rotor 3, blades 4, a left end cover 5, a right end cover 6, a spring 6, a right machine shell 1 and a transmission shaft 7.
The motor casing of this embodiment mainly comprises: the motor comprises a left casing 1-1 and a right casing 1, wherein the casing of the motor is internally provided with a cylindrical cavity, the left casing comprises an injection port 91 for high-pressure working fluid, and the right casing comprises a discharge port 92 for low-pressure working fluid (see figure 1 in detail).
The mutual positions of the installation of the main components constituting the hydraulic vane motor movement are as follows: a stator 2 (detailed figures 2 and 3), a stator built-in rotor 3 (detailed figures 2 and 3), blades 4 (detailed figures 2 and 3) capable of performing radial displacement are arranged in each rotor blade groove, a plurality of blade grooves with radial inclination angles are arranged on the peripheral wall of the rotor at intervals along the circumferential direction, and a left end cover 5 and a right end cover 5-1 (detailed figures 2 and 3) are arranged at two axial ends of the stator; a groove bottom cavity 89 (detailed in figures 21 and 22) is correspondingly formed between the tail part of each blade, the bottom of the blade groove and the two end covers, and a working cavity 88 (detailed in figures 21 and 22) is correspondingly formed between each pair of two adjacent blades (in action period) extending radially, a rotor, a stator and the two end covers; the machine core consists of a rotor, blades, a stator and two end covers;
in the hydraulic vane motor core in the embodiment, the surface of the inner cavity of the stator comprises two groups of two variable-diameter sections with the distance from the axis of the core changing circumferentially; the movement comprises: the injection port can be communicated with an extension injection port of the working cavity contacted with one of the reducing sections, the discharge port can be communicated with an extension discharge port of the working cavity contacted with the other reducing section, and the extension injection port and the extension discharge port are circumferentially arranged in a separated mode and cannot be communicated with the same working cavity at the same time; the diameter-changing section corresponding to the extension injection port is an expanding section, and the diameter-changing section corresponding to the extension discharge port is a reducing section;
the machine core is a mechanism which converts the pressure energy of high-pressure working fluid in a working cavity communicated with the extension injection port into mechanical energy for driving the rotor to rotate, and the rotor rotates towards the working cavity with larger volume in the process that two adjacent working cavities corresponding to the same blade simultaneously contact with the diameter-expanding section; a transmission shaft penetrates through the core of the hydraulic vane motor, and a rotor in the core drives the transmission shaft 7 to work (as shown in figure 1);
the structure of the main parts in the movement is described in detail as follows with reference to the attached drawings of the specification:
fig. 4 to 6 show the left end cap 5 adopted in this embodiment, a pair of extended discharge ports 93 communicating with the working chambers, a pair of extended injection ports 94 communicating with the working chambers, a pair of tank bottom cavity liquid outlet auxiliary channels 95 communicating with the working chambers on the front and rear sides and simultaneously having an included angle of α 3 with respect to the whole circumferential range of the extended discharge ports, and a pair of tank bottom cavity liquid inlet auxiliary channels 96 communicating with the working chambers on the smaller side and having an included angle of α 4 with respect to the circumferential range of the extended injection ports, are circumferentially spaced from each other on an end plane corresponding to the stator of the left end cap, the tank bottom cavity liquid outlet auxiliary channels dispose low-pressure working liquid to axially communicated tank bottom cavities, and the tank bottom cavity liquid inlet auxiliary channels dispose high-pressure working liquid to axially communicated tank bottom cavities.
Fig. 7 to 9 show the stator adopted in this embodiment, the inner surface of the stator includes two expanding sections α 5, two reducing sections α 6, two connecting sections from the expanding section to the reducing section large arc R, and two connecting sections from the reducing section to the expanding section small arc R1, the discharge port 93 extending from the corresponding end cap is provided with a pair of liquid outlet matching channels 97 having an included angle α 1 and two chutes 972 at the front and rear sides from the inner surface to the outer diameter of the stator, the injection port 94 extending from the corresponding end cap is provided with a pair of liquid inlet matching channels 98 having an included angle α 2 and two chutes 982 at the front and rear sides from the inner surface of the stator, a discharge port 921 is provided between the discharge port and the injection port, and a discharge port direct-coupling channel 911 is provided between the injection port and the injection port in the stator, the liquid outlet matching channel is correspondingly provided with low-pressure working liquid P1 for the bottom cavity balance liquid distribution channel, and the liquid inlet matching channel is correspondingly provided with high-pressure working liquid P2 for the bottom cavity balance liquid distribution channel. (the angles of α 1 and α 2 and the angles of α 5 and α 6 are designed according to actual conditions)
Fig. 10 to 12 show a right end cap 5-1 adopted in this embodiment, the right end cap and the left end cap are correspondingly provided with a partition: a pair of extended discharge openings 93, a pair of extended filling opening blind grooves 941, a pair of groove bottom cavity liquid outlet auxiliary channels 95 and a pair of groove bottom cavity liquid inlet auxiliary channel blind grooves 961.
Fig. 13 to 15 show the rotor 3 adopted in the present embodiment, the rotor has an outer diameter R2, 16 vane grooves 31 having an inclination angle of 0 degree in the radial direction are formed in the rotor, two spring holes 61 are axially formed at the bottom of each vane groove, and a spring 6 is disposed in each spring hole (see fig. 21 and 22).
Referring to fig. 16 to 22, the blade of the present embodiment is characterized in that the head of the blade is provided with at least a front correction angle and a rear correction angle capable of contacting the inner surface of the stator corresponding to the rotation direction of the rotor, a middle portion of the head of the blade is formed between the top ends of the front correction angle and the rear correction angle, and when the blade extends out of the inner surface of the stator at the one correction angle, the side working cavity adjacent to the side correction angle in the blade and the middle portion of the head of the blade form the side clearance channel; the adopted blade 4 is characterized in that a plurality of contact positions between the head part and the inner surface of the stator with the maximum radius are required, and a plurality of correction angles are arranged at the head part, as shown in detail in figure 21;
the blade is provided with a groove bottom cavity balance liquid distribution channel 83 which consists of a groove formed in the middle part of the head of the blade and the inner diameter of the groove, and 4 axially distributed holes which penetrate from the groove to the tail of the blade (the number of the axially distributed holes can be increased or reduced according to the experience of professional engineers).
In the embodiment shown in fig. 21, for any blade located at the maximum radial position and having the rear working chamber communicated with the extension inlet and the front working chamber communicated with the extension outlet, the pressure difference between the two working chambers and the movement gap between the side surface of the blade and the side surface of the blade slot of the rotor cause the blade to generate at least a blade front correction angle to contact with the inner surface of the stator, when a plurality of correction angles of the head of the blade simultaneously contact with the inner surface of the stator in the section, the length of the contact is increased by times, and the contact stress generated between the correction angle of the head of the blade at the contact position and the inner surface of the stator is correspondingly reduced; and hydraulic force for contacting the rear correcting angle of the blade with the inner surface of the stator is at least generated by the pressure difference of the working cavities at two sides and the movement clearance between the side surface of the blade and the side surface of the rotor blade groove corresponding to any blade which is positioned at the minimum radial position and is communicated with the front working cavity of the extension discharge outlet and the extension filling opening.
In this embodiment, the tank bottom cavity intermittent liquid distribution channel for distributing liquid to the tank bottom cavity is divided into: the second type of tank bottom cavity intermittent liquid distribution channel is arranged between the corresponding tank bottom cavity and the front side working cavity and used for enabling the corresponding tank bottom cavity in synchronous rotary displacement to be intermittently communicated with the front side working cavity, and the first type of tank bottom cavity intermittent liquid distribution channel is arranged between the corresponding tank bottom cavity and the rear side working cavity and used for enabling the corresponding tank bottom cavity in synchronous rotary displacement to be intermittently communicated with the rear side working cavity.
See fig. 16-23 in this embodiment, two types of tank bottom cavity intermittent liquid distribution channels are adopted in the matching group: two second-type tank bottom cavity intermittent liquid distribution channels I8111 which are integrally arranged in the corresponding middle blades are axially arranged corresponding to the axial separation between the front side working cavity and the corresponding tank bottom cavity, and two first-type tank bottom cavity intermittent liquid distribution channels I8211 which are integrally arranged in the corresponding middle blades are axially arranged corresponding to the axial separation between the rear side working cavity and the corresponding tank bottom cavity.
In each action period, each blade has a pair of processes of expansion and retraction, the difference value of the maximum radial distance from the head of the blade to the axle center of the rotor and the minimum radial distance is firstly drawn up as the numerical value (h) of the radial telescopic distance of the blade, and in the embodiment, the numerical value is used as the basic comparison parameter for designing the radial position of the intermittent liquid distribution channel of the tank bottom cavity.
See fig. 23, the carrier blade is set at the maximum radial position, when the illustrated carrier blade is taken as the rear blade of the front working chamber (the middle corresponding blade of the front working chamber is the blade on the corresponding tank bottom chamber), a second type of tank bottom chamber intermittent liquid distribution channel one 8111 is set, and when the illustrated carrier blade is taken as the front blade of the rear working chamber, a first type of tank bottom chamber intermittent liquid distribution channel one 8211 is set:
the first groove bottom cavity intermittent liquid distribution channel 8111 is arranged as follows: when the vane shown in fig. 23 is used as the middle corresponding vane description of the front side working chamber, a virtual boundary line is set at a value of about 1/4 radial expansion and contraction distances of the vane by radially displacing a boundary line 343 where the corresponding groove bottom chamber intersects with the front side surface of the vane groove in the vane, and the virtual boundary line is corresponding to the corresponding position of the front side surface of the middle corresponding vane to serve as a radial starting boundary 3431 of the second type groove bottom chamber intermittent liquid distribution channel I8111 and open the vane head in a groove form towards the outer diameter.
The first type of groove bottom cavity intermittent liquid distribution channel 8211 is arranged: when the vane shown in fig. 23 is used as a middle corresponding vane of the rear working chamber, a boundary line 342 where the rear side surface of the rear vane slot of the rear working chamber and the radial outer surface of the rotor intersect is displaced outwards by about 3/4 values of the radial expansion distance of the vane to set a virtual boundary line, and the virtual boundary line is corresponding to the corresponding position of the front side surface of the middle corresponding vane to serve as a radial starting boundary of a first-type slot bottom cavity intermittent liquid distribution channel 8211 and open the tail of the vane towards the inner diameter in a slotted mode.
The liquid passageway major structure is joined in marriage to this embodiment groove bottom chamber includes: the blade of the machine core and the rotor are provided with a second groove bottom cavity intermittent liquid distribution channel, a first groove bottom cavity intermittent liquid distribution channel and a groove bottom cavity balance liquid distribution channel.
The balanced liquid distribution channel of the tank bottom cavity can enable the working liquid pressure in the middle part of the head part of the blade and the corresponding tank bottom cavity to be relatively balanced.
Referring to point 245 in fig. 21, the extended discharge port makes the rear part of the blade head divided by the axial contact line of the correction angle of the rear side of the blade head and the inner surface of the stator contact low-pressure working fluid, and the extended injection port, the tank bottom cavity balanced fluid distribution channel and the first type of tank bottom cavity intermittent fluid distribution channel make the rest part of the blade head and the blade tail contact high-pressure working fluid, and the radial area of the rear part of the blade head is designed according to the hydraulic demand of the blade maintaining the outward radial expansion trend; referring to 248 in fig. 21, the extended outlet makes the front correction angle of the blade head contact the axial line of the stator inner surface to define the front part of the blade head contacting the low pressure working fluid, while the extended inlet, the tank bottom cavity balance fluid distribution channel and the second tank bottom cavity intermittent fluid distribution channel make the rest part of the blade head and the blade tail contacting the high pressure working fluid, and the radial area of the front part of the blade head is designed according to the hydraulic demand for maintaining the blade to stretch to the outer diameter. (the radial areas of the rear and front portions of the blade head can be appropriately adjusted according to the experience of a professional engineer.)
Referring to fig. 21 and 22, the main path that the corresponding slot bottom cavity 89 communicates with the front side working cavity or/and the rear side working cavity when the correction angle of the blade head contacts different circumferential nodes with the inner surface of the stator is shown, and correspondingly, the comparison between the hydraulic force for extending the blade outward in the radial direction obtained at the tail part of the blade and the total hydraulic force for retracting the blade inward in each part of the blade head is shown:
in operation, as shown in point 241 in fig. 22, the rear working cavity is separated from the discharge port and is not communicated with the extension injection port, the rear working cavity maintains relatively low working fluid pressure, the front working cavity maintains communication with the extension injection port, the corresponding tank bottom cavity communicates with the front working cavity through the first tank bottom cavity intermittent liquid distribution channel 8111, the middle part of the blade head communicates with the corresponding tank bottom cavity through the balance channel, so that the front part of the blade head, the middle part of the blade head and the blade tail contact high-pressure working fluid P2, and the rear part of the blade head contacts relatively low-pressure working fluid, as shown in the figure, the hydraulic force for extending the blade towards the outer diameter is obtained at the blade tail and is greater than the total hydraulic force for retracting the blade towards the inner diameter at the blade head, and the hydraulic force for extending the blade towards the outer diameter is obtained at the blade on the corresponding tank bottom cavity;
see 242 points in fig. 22, the front and rear working cavities are simultaneously communicated with the extension injection port, the corresponding bottom cavity of the groove is kept communicated with the front working cavity through the second type side groove bottom cavity intermittent liquid distribution channel I8111, the corresponding tank bottom cavity is communicated with the rear working cavity through a first type side tank bottom cavity intermittent liquid distribution channel 8221, the two types of tank bottom cavity intermittent liquid distribution channels start the alternate switching of the respective communication working conditions, the corresponding tank bottom cavity can be communicated with the front side working cavity through a tank bottom cavity balance liquid distribution channel 83, the middle part of the blade head and the front side clearance channel, the middle part of the blade head is communicated with the corresponding tank bottom cavity through a balance channel, thus, all parts of the head part of the blade and the tail part of the blade are contacted with high-pressure working fluid P2, the hydraulic force for enabling the blade to stretch outwards and radially obtained by the tail part of the blade as shown in the figure is basically the same as the total hydraulic force for enabling the blade to retract inwards and radially obtained by all parts of the head part of the blade, and the hydraulic force for enabling the blade to stretch outwards and radially obtained by the blade on the corresponding groove bottom cavity is not obtained;
at point 243 in fig. 22, the front and rear working chambers are simultaneously communicated with the extension injection port, the corresponding tank bottom chamber is kept communicated with the rear working chamber through a first type tank bottom chamber intermittent liquid distribution channel I8211, the corresponding tank bottom cavity is communicated with the front side working cavity through a second type side tank bottom cavity intermittent liquid distribution channel I8111, the two types of tank bottom cavity intermittent liquid distribution channels complete the alternate switching of the respective communication working conditions, the corresponding tank bottom cavity can be communicated with the front side working cavity through a tank bottom cavity balance liquid distribution channel 83, the middle part of the blade head and the front side clearance channel, the middle part of the blade head is communicated with the corresponding tank bottom cavity through a balance channel, thus, all parts of the head part of the blade and the tail part of the blade are contacted with high-pressure working fluid P2, the hydraulic force for enabling the blade to stretch outwards and radially obtained by the tail part of the blade as shown in the figure is basically the same as the total hydraulic force for enabling the blade to retract inwards and radially obtained by all parts of the head part of the blade, and the hydraulic force for enabling the blade to stretch outwards and radially obtained by the blade on the corresponding groove bottom cavity is not obtained;
at 244 of fig. 22, the rear working chamber is communicated with the extension injection port, the front working chamber is separated from the injection port and is not communicated with the extension discharge port, the front working chamber maintains relatively high working fluid pressure, the corresponding tank bottom chamber is communicated with the rear working chamber through a first-type tank bottom chamber intermittent liquid distribution channel I8211, the middle part of the head of the blade is communicated with the corresponding tank bottom chamber through a balance channel, so that the rear part of the head of the blade, the middle part of the head of the blade and the tail of the blade contact high-pressure working fluid P2, and the front part of the head of the blade contacts the working fluid with relatively high pressure;
at point 245 in fig. 21, the rear working chamber is communicated with the extension injection inlet, the front working chamber is communicated with the extension discharge outlet, the corresponding tank bottom chamber is communicated with the rear working chamber through a first tank bottom chamber intermittent liquid distribution channel 8211, the middle part of the blade head is communicated with the corresponding tank bottom chamber through a balance channel, so that the rear part of the blade head, the middle part of the blade head and the blade tail are contacted with high-pressure working liquid P2, while the front part of the blade head is contacted with low-pressure working liquid P1, as shown in the figure, the hydraulic force for expanding the blade towards the outer diameter is obtained by the blade tail and is greater than the total hydraulic force for contracting the blade towards the inner diameter obtained by the parts of the blade head, and the hydraulic force for expanding the blade towards the outer diameter is obtained by the blade on the corresponding tank bottom chamber;
at point 246 shown in fig. 22, the front and rear working chambers are simultaneously communicated with the extended discharge port, the corresponding tank bottom chamber is kept communicated with the rear working chamber through a first type tank bottom chamber intermittent liquid distribution channel I8211, the corresponding tank bottom cavity starts to be communicated with the front side working cavity through a first type side tank bottom cavity intermittent liquid distribution channel 8111, the two types of tank bottom cavity intermittent liquid distribution channels start to be communicated with the working conditions and are switched alternately again, the corresponding tank bottom cavity can be communicated with the rear side working cavity through a tank bottom cavity balance liquid distribution channel 83, the middle part of the blade head and the rear side clearance channel, the middle part of the blade head is communicated with the corresponding tank bottom cavity through a balance channel, thus, all parts of the head part of the blade and the tail part of the blade are contacted with low-pressure working fluid P1, the hydraulic force for enabling the blade to stretch outwards and radially obtained by the tail part of the blade as shown in the figure is basically the same as the total hydraulic force for enabling the blade to retract inwards and radially obtained by all parts of the head part of the blade, and the hydraulic force for enabling the blade to stretch outwards and radially obtained by the blade on the corresponding groove bottom cavity is not obtained;
at point 247 in fig. 22, the front and rear working cavities are simultaneously communicated with the extended discharge port, the corresponding tank bottom cavity is kept communicated with the front working cavity through the second-type side tank bottom cavity intermittent liquid distribution channel I8111, the corresponding tank bottom cavity is communicated with the rear working cavity through the first-type tank bottom cavity intermittent liquid distribution channel I8211, and the two-type tank bottom cavity intermittent liquid distribution channels complete the re-alternate switching of the respective communication working conditions; the corresponding tank bottom cavity can be communicated with the rear side working cavity through a tank bottom cavity balance liquid distribution channel 83, the middle part of the head of the blade and a rear side clearance channel, the middle part of the head of the blade is communicated with the corresponding tank bottom cavity through a balance channel, so that all parts of the head of the blade and the tail of the blade are contacted with low-pressure working liquid P1, the hydraulic force for enabling the blade to stretch outwards and radially obtained by the tail of the blade is basically the same as the total hydraulic force for enabling the blade to retract inwards and radially obtained by all parts of the head of the blade, and the hydraulic force for enabling the blade to stretch outwards and radially obtained by the blade on the corresponding tank bottom cavity is not obtained by the blade on the corresponding tank bottom cavity;
at 248 in fig. 21, the rear working chamber is communicated with the extension outlet, the front working chamber is communicated with the extension inlet, the corresponding tank bottom chamber is communicated with the front working chamber through a first intermittent liquid distribution channel 8111 of the second type of side tank bottom chamber, the middle part of the blade head is communicated with the corresponding tank bottom chamber through a balance channel, so that the front part of the blade head, the middle part of the blade head and the blade tail are contacted with high-pressure working liquid P2, and the rear part of the blade head is contacted with low-pressure working liquid P1;
and starting when the front side working cavity is separated from the discharge port, entering the next working cycle and repeating.
The two types of tank bottom cavity intermittent liquid distribution channels enable the corresponding tank bottom cavity to be respectively communicated with the rear side working cavity and the front side working cavity in an alternating mode, and the corresponding tank bottom cavity is switched to be communicated with the front side working cavity from the communicated rear side working cavity in an alternating mode by utilizing the rear side clearance channel and the front side clearance channel in the middle of the head part of the blade clamped by the front side working cavity and the rear side working cavity and correspondingly through the rear side working cavity and the front side working cavity communicated and extended injection port in a rotating displacement mode; in the alternative switching process, the corresponding groove bottom cavity can be communicated with the extension filling opening through a liquid inlet and distribution channel in the left end cover to obtain high-pressure working liquid.
Referring to fig. 21 and 22, in the whole action cycle, the main structure of the tank bottom cavity intermittent liquid distribution channel enables the corresponding tank bottom cavity to be communicated with at least one corresponding working cavity, so that the main structure of the tank bottom cavity intermittent liquid distribution channel enables the corresponding tank bottom cavity to continuously obtain optimized liquid distribution with adjustable pressure from the corresponding communicated working cavity; referring to fig. 4, 5, 10, 11, 21 and 22, in the whole action period, when the groove bottom cavity 89 contacts the groove bottom cavity liquid outlet auxiliary channel 95 with the included angle of α 3 in the end cover, the channel sectional area of the discharged low-pressure working liquid P1 can be increased, and when the groove bottom cavity 89 contacts the groove bottom cavity liquid inlet auxiliary channel 96 with the included angle of α 4 in the end cover, the high-pressure working liquid P2 can be obtained.
The radial boundary line and the effective sectional area after the numerical value comparison of the radial telescopic distance of the blades in the intermittent liquid distribution channel of the bottom cavity of the tank is set can be changed and adjusted within a certain range by a person skilled in the art according to the technical requirements, and the specific positions and the effective sectional areas of other channels in the intermittent liquid distribution channel structure of the bottom cavity of the tank can be changed and adjusted within a certain range; the corresponding tank bottom cavity guides low-pressure working liquid into the cavity through the corresponding working cavity during volume expansion, and the corresponding tank bottom cavity discharges high-pressure working liquid in the cavity to the outside of the motor through the corresponding working cavity during volume reduction; the tank bottom cavity liquid distribution channel structure leads all the working liquid flow generated in the process that the corresponding tank bottom cavity works in the volume change to be summarized into the effective displacement of the motor; thereby improving the volumetric efficiency of the hydraulic vane motor of the present embodiment.
Referring to fig. 21 and 22, in the whole action cycle, the vanes on the corresponding groove bottom cavities mainly utilize the hydraulic force to keep the vanes moving towards the outer diameter direction in the section obtaining the outer diameter stretching hydraulic force; the corresponding blade on the groove bottom cavity keeps the trend of moving towards the outer diameter direction mainly by utilizing the driving force consisting of centrifugal force generated by the blade in working and proper working load preset by a spring in a hydraulic section which does not obtain or basically does not obtain the outward diameter extension; the working load of the spring can be adjusted more practically and with the experience of a professional engineer.
The working load preset by the groove bottom cavity liquid distribution channel structure and the spring of the hydraulic vane motor of the embodiment firstly ensures that at least one side correction angle of each vane head in the working process always keeps proper contact stress with the inner surface of the stator, so that the failure problem caused by abrasion of the inner surface of the stator is improved, and the working pressure of the hydraulic vane motor of the embodiment is improved.
Example 2: referring to fig. 1-23, the present embodiment is a double acting hydraulic vane motor;
referring to fig. 7 to 9, for convenience of processing, the difference from embodiment 1 is that in this embodiment, two chutes 972 are removed from the stator liquid outlet matching passage 97 and two chutes 982 are removed from the stator liquid inlet matching passage 98, and 971 in the liquid outlet matching passage with a smaller included angle is used to replace the description of the liquid outlet matching passage 97 and 981 in the liquid inlet matching passage with a smaller included angle is used to replace the description of the liquid inlet matching passage 98.
The rest corresponds to those described in example 1.
Example 3: referring to fig. 1-23, the present embodiment is a double acting hydraulic vane motor;
referring to fig. 7 and 8, the difference from embodiment 1 is that, corresponding to the lower rated rotation speed of the hydraulic vane motor: in this embodiment, after the pair of liquid outlet matching channels 97 is removed from the inner surface of the stator, when the total actual effective cross-sectional area of the remaining liquid distribution channels can also meet the liquid outlet flow rate requirement of the corresponding tank bottom cavity in the process of increasing the volume, the pair of liquid outlet matching channels 97 is removed from the inner surface of the stator, so that no corresponding statement is made on the removed channels in this embodiment.
The rest corresponds to that described in example 1.
Example 4: referring to fig. 1-23, the present embodiment is a double acting hydraulic vane motor;
referring to fig. 7 and 8, the difference from embodiment 1 is that, corresponding to the lower rated rotation speed of the hydraulic vane motor: in this embodiment, after the pair of liquid inlet matching channels 98 is removed from the inner surface of the stator, when the total actual effective cross-sectional area of each remaining liquid distribution channel can also meet the liquid inlet flow rate requirement of the corresponding groove bottom cavity in the volume reduction process, the pair of liquid inlet matching channels 98 is removed from the inner surface of the stator, so that no corresponding statement is made on the removed channels in this embodiment.
The rest corresponds to that described in example 1.
Example 5: referring to fig. 1-23, the present embodiment is a double acting hydraulic vane motor; referring to fig. 7 and 8, when the vector gradient of the inner surface of the corresponding stator is large, and the maximum sectional area of the clearance channel between the middle part of the blade head and the corresponding working cavity is larger than the total sectional area of the balanced liquid distribution channel of the bottom cavity of the distribution groove, the difference from the embodiment 1 is that a pair of liquid outlet matching channels 97 and a pair of liquid inlet matching channels 98 are omitted from the stator, so that the omitted channels are not described again in the embodiment.
The rest corresponds to that described in example 1.
Example 6: referring to fig. 1-23, the present embodiment is a double acting hydraulic vane motor;
fig. 4, 5, 10, 11 correspond to a lower rated speed of the hydraulic vane motor, which is different from that of embodiment 1: in this embodiment, a pair of groove bottom cavity liquid inlet auxiliary channels 96 are removed from the left end cover 5, correspondingly, a pair of blind grooves 961 are removed from the right end cover 5-1, and when the total actual effective sectional area of the remaining liquid distribution channels can meet the liquid outlet flow rate requirement of the corresponding groove bottom cavity in the volume increasing process, the pair of groove bottom cavity liquid inlet auxiliary channels 96 are removed from the left end cover 5, and correspondingly, the pair of blind grooves 961 are removed from the right end cover 5-1, so that the corresponding description is not provided for the removed channels in this embodiment; the groove bottom cavity liquid distribution channel structure replaces and cancels a liquid distribution channel of high-pressure working liquid arranged in a left end cover and a right end cover of a vane motor, so that internal leakage increased in a movement gap between two axial planes of a core rotating part and corresponding planes of the two end covers is partially eliminated.
The rest corresponds to that described in example 1.
Example 7: referring to fig. 1-23, the present embodiment is a double acting hydraulic vane motor;
fig. 4, 5, 10, 11 correspond to a lower rated speed of the hydraulic vane motor, which is different from that of embodiment 1: in this embodiment, a pair of tank bottom cavity liquid outlet auxiliary channels 95 and a pair of tank bottom cavity liquid inlet auxiliary channels 96 are removed from the left end cover 5, correspondingly, a pair of tank bottom cavity liquid outlet auxiliary channels 95 and a pair of blind grooves 961 are removed from the right end cover 5-1, and when the total actual effective sectional area of the remaining liquid distribution channels can meet the requirement of the liquid distribution flow rate of the corresponding tank bottom cavity in the volume change process, the pair of tank bottom cavity liquid outlet auxiliary channels 95 and the pair of tank bottom cavity liquid inlet auxiliary channels 96 are removed from the left end cover 5, and correspondingly, the pair of tank bottom cavity liquid outlet auxiliary channels 95 and the pair of blind grooves 961 are removed from the right end cover 5-1, so that corresponding descriptions are not provided for the removed channels in this embodiment; the groove bottom cavity liquid distribution channel structure replaces and cancels a liquid distribution channel of high-pressure and high-pressure working liquid arranged in a left end cover and a right end cover of a vane motor, so that internal leakage increased in a motion gap between two axial planes of a core rotating part and corresponding planes of the two end covers is completely eliminated.
The rest corresponds to that described in example 1.
Example 8: referring to fig. 1 and 3, fig. 24 to 40 show a single-acting hydraulic vane motor according to the present embodiment; it mainly comprises: the device comprises a left machine shell 1-1, a stator 2, a rotor 3, blades 4, a left end cover 5, a right end cover 6, a spring 6, a right machine shell 1 and a transmission shaft 7.
The motor casing of this embodiment mainly comprises: the left casing 1-1 and the right casing 1, the casing of the motor has a cylindrical cavity, the left casing contains an inlet 91 for high pressure working fluid, and the right casing contains an outlet 92 for low pressure working fluid (see fig. 1).
The mutual positions of the installation of the main components that make up the hydraulic vane motor movement: the stator 2 (detailed shown in figure 27), the stator built-in rotor 3 (detailed shown in figure 36), the blades 4 (detailed shown in figures 31-35) which can be displaced in the radial direction are built in each rotor blade groove, and the left end cover 5 and the right end cover 5-1 (detailed shown in figures 25, 26, 29 and 30) are arranged at the two axial ends of the stator; a groove bottom cavity 89 (detailed in figures 38, 39 and 40) is correspondingly formed among the tail part of each blade, the bottom part of the blade groove and two end covers, and a working cavity 88 (detailed in figures 38, 39 and 40) is correspondingly formed among each pair of two adjacent blades, a rotor, a stator and two end covers which radially extend (in action period); the machine core consists of a rotor, blades, a stator and two end covers;
in the hydraulic vane motor core in the embodiment, the surface of the inner cavity of the stator comprises a group of two variable diameter sections with the distance from the axis of the core changing circumferentially; the movement comprises: the injection port can be communicated with an extension injection port of the working cavity contacted with one of the reducing sections, the discharge port can be communicated with an extension discharge port of the working cavity contacted with the other reducing section, and the extension injection port and the extension discharge port are circumferentially arranged in a separated mode and cannot be communicated with the same working cavity at the same time; the diameter-changing section corresponding to the extension injection port is an expanding section, and the diameter-changing section corresponding to the extension discharge port is a reducing section;
the machine core is a mechanism which converts the pressure energy of high-pressure working fluid in a working cavity communicated with the extension injection port into mechanical energy for driving the rotor to rotate, and the rotor rotates towards the working cavity with larger volume in the process that two adjacent working cavities corresponding to the same blade simultaneously contact with the diameter-expanding section; a transmission shaft penetrates through the core of the hydraulic vane motor, and a rotor in the core drives the transmission shaft 7 to work (as shown in figure 1);
the structure of the main parts in the movement is described in detail as follows with reference to the attached drawings of the specification:
fig. 25 and 26 show the left end cap 5 adopted in this embodiment, an extended discharge port 93 communicating with the working cavity, an extended injection port 94 communicating with the working cavity, and a groove bottom cavity liquid inlet auxiliary channel 96 corresponding to the circumferential range included angle α 4 smaller than the circumferential range of the extended injection port communicating with the working cavity on one side are circumferentially arranged on the end plane corresponding to the stator of the left end cap, and the groove bottom cavity liquid inlet auxiliary channel is configured with high-pressure working liquid P2 to the axial end of the communicated groove bottom cavity.
Fig. 27 and 28 show that the present embodiment adopts a stator 2 including an expanding section with an included angle α 5, a reducing section with an included angle α 6, a large circular arc R of a connecting section from the expanding section to the reducing section, and a small circular arc R1 of a connecting section from the reducing section to the expanding section, a liquid outlet matching channel 97 with an included angle α 1 and inclined slots 972 at the front and rear sides is arranged from the inner surface to the outer diameter of the stator corresponding to a liquid outlet 93 extending from an end cap, and a liquid inlet matching channel 98 with an included angle α 2 and inclined slots 982 at the front and rear sides is arranged from the inner surface to the outer diameter of the stator corresponding to an injection port 94 extending from an end cap; the liquid outlet matching channel is provided with low-pressure working liquid P1 for the bottom cavity balance liquid distribution channel, and the liquid inlet matching channel is provided with high-pressure working liquid P2 for the bottom cavity balance liquid distribution channel.
Fig. 29 and 30 show a right end cap 5-1 adopted in the present embodiment, where the right end cap and the left end cap are correspondingly provided with: an extended discharge hole 93, an extended filling opening blind groove 941 and a groove bottom cavity liquid inlet auxiliary channel blind groove 961.
See fig. 36 and 37, which show the rotor 3 of the present embodiment, the rotor has an outer diameter R2, 15 blade grooves 31 are formed in the rotor, the radial direction θ of which is set to be a radial inclination angle of 5 degrees as shown in fig. 47 with respect to the radial direction and the working direction,
fig. 31 to 35 show a vane 4 used in this embodiment, where the vane is placed in a vane slot of a rotor and has a same inclination angle with the vane slot of the rotor, a difference obtained by subtracting one half of the telescopic distance of the vane from the larger radius of the rotor axis corresponding to the inner surface of the stator is a radius, and the rotor axis is a virtual circle as a center of the circle, the vane of this embodiment adopts a head capable of contacting with the virtual circle at the same time as a requirement for setting front and rear side correction angles, a middle part of the vane head is formed between the top ends of the front and rear side correction angles, a groove is axially formed in the middle part of the vane head in the radial direction, and when the extended vane is separated from the inner surface of the stator at one side correction angle, the side working cavity adjacent to the side correction angle in the vane and the middle part of the vane head form a side clearance channel;
the arrangement of the tank bottom cavity balance liquid distribution channel: two groove bottom cavity balance liquid distribution channels 83 axially distributed from the inner diameter in the groove at the head of the blade are arranged in the blade; a tank bottom cavity balance liquid distribution channel 84 is axially arranged in the center of the radial position of the corresponding blade on the maximum position, and a tank bottom cavity balance liquid distribution channel 841 of the blade part and a tank bottom cavity balance liquid distribution channel 842 of the rotor part form a tank bottom cavity balance liquid distribution channel 84; the blade part 841 is provided with a blind hole from the middle part of the blade head to the tail part of the blade, and is provided with a hole on the front side surface of the blade to communicate with the blind hole, the radial lower edge of the hole on the front side surface of the blade reaches the boundary line of the intersection of the rear side surface of the rotor blade groove and the bottom arc surface of the rotor blade groove, the radial expansion distance of the blade is about 2/3, the front side surface of the rotor blade groove is provided with a rotor part groove bottom cavity balance liquid distribution channel 842 in a slotted mode, the boundary line of the intersection of the front side surface of the rotor blade groove and the bottom arc surface of the rotor blade groove is about 1 radial expansion distance of the blade, the back of the corresponding rotor blade slot is used as the radial starting boundary of the rotor part slot bottom cavity balance liquid distribution channel 842, and the rotor part slot bottom cavity balance liquid distribution channel 842 is opened to the corresponding slot bottom cavity in the inner radial direction (the slot bottom cavity balance liquid distribution channel increases or decreases the number of holes according to the experience of professional engineers);
the two radial tail ends of the tank bottom cavity balance liquid distribution channel 83 are expanded with spring holes 61, and springs 6 are arranged in the spring holes (see fig. 38).
The small stator circular arc R1 is larger than the rotor outer diameter R2.
In the embodiment, corresponding to any blade which is positioned at the maximum radial position and is communicated with the extension injection port and the extension discharge port by the rear working cavity, a front correction angle of the blade is determined to be generated to be contacted with the inner surface of a stator mainly by a radial inclination angle limited by a rotor blade groove to the blade, and a rear clearance channel is formed between the middle part of the head of the blade and the rear working cavity; the rear side correcting angle of the blade is mainly determined by the radial inclination angle of the rotor blade groove to the blade to contact with the inner surface of the stator, and a front side clearance channel is formed between the middle part of the head of the blade and the front side working cavity.
In this embodiment, the tank bottom cavity intermittent liquid distribution channel for liquid distribution to the tank bottom cavity is divided into: the first type of tank bottom cavity intermittent liquid distribution channel is arranged between the corresponding tank bottom cavity and the front side working cavity and used for enabling the corresponding tank bottom cavity in synchronous rotary displacement to be intermittently communicated with the front side working cavity, and the second type of tank bottom cavity intermittent liquid distribution channel is arranged between the corresponding tank bottom cavity and the rear side working cavity and used for enabling the corresponding tank bottom cavity in synchronous rotary displacement to be intermittently communicated with the rear side working cavity.
See fig. 31-40 in this embodiment, two types of tank bottom cavity intermittent liquid distribution channels are adopted in the matching group: a second type of groove bottom cavity intermittent liquid distribution channel II 8122 is axially and centrally arranged between the corresponding front side working cavity and the corresponding groove bottom cavity, is partially arranged in a front side blade of the front side working cavity and is partially arranged in the rotor, and a first type of groove bottom cavity intermittent liquid distribution channel II 8222 is axially and centrally arranged between the corresponding rear side working cavity and the corresponding groove bottom cavity, is partially arranged in a rear side blade of the rear side working cavity and is partially arranged in the rotor.
Referring to fig. 40, the carrier blade is set at the maximum radial position, when the illustrated carrier blade is taken as the front blade in the front direction of the front working chamber, a second type of tank bottom chamber intermittent liquid distribution channel 8122 is set, when the illustrated carrier blade is taken as the rear blade in the rear direction of the rear working chamber and when the illustrated carrier blade is taken as the middle corresponding blade in the front direction of the rear working chamber, a second type of tank bottom chamber intermittent liquid distribution channel 8222 is set:
when the vane shown in fig. 40 is used as the front vane of the front working chamber, a virtual boundary line is set by the value that the boundary line 342 of the intersection of the rear side surface of the front vane groove of the front working chamber and the radial outer surface of the rotor is radially displaced outwards by about 11/20 radial expansion distances of the vane, and the virtual boundary line is corresponding to the corresponding position of the rear side surface of the front vane of the front working chamber and is used as the radial starting boundary 3421 of the second-type groove bottom chamber intermittent liquid distribution passage two 81221 of the vane part, and the head of the vane is opened outwards in a groove form; a virtual boundary line is set at the value of 1/4 blade radial expansion distance of the boundary line 342 of the intersection of the rear side surface of the front side blade groove of the front side working cavity and the radial outer surface of the rotor, the virtual boundary line is corresponding to the corresponding position of the rear side surface of the front side blade groove of the front side working cavity to be used as the radial starting boundary 3422 of the platform of the second type of tank bottom cavity intermittent liquid distribution channel II 81222, a virtual boundary line is set at the value of 1 blade radial expansion distance of the boundary line 342 of the intersection of the rear side surface of the front side blade groove of the front side working cavity and the radial outer surface of the rotor to be used as the radial ending boundary 3423 of the platform of the second type of tank bottom cavity intermittent liquid distribution channel II 81222, holes of the second type of tank bottom cavity intermittent liquid distribution channel II 81222 are arranged in the form of holes, and are opened from the platform to the corresponding tank bottom cavity, the platform and the hole form a second groove bottom cavity intermittent liquid distribution channel II 81222 of the rotor part; (ii) a The second type of groove bottom cavity intermittent liquid distribution channel II 81221 of the blade part and the second type of groove bottom cavity intermittent liquid distribution channel II 81222 of the rotor part form a second type of groove bottom cavity intermittent liquid distribution channel II 8122, the first portion of which is arranged in the front side working cavity front side blade, and the second portion of which is arranged in the rotor.
The second 8222 of the intermittent liquid distribution channel of the bottom cavity of the first type of groove is arranged: when the vane shown in fig. 40 is used as the rear vane of the rear working chamber, a virtual boundary line is set by displacing a boundary line 341 intersecting the front side surface of the rear vane groove of the rear working chamber by about 1/5 radial expansion and contraction distances of the vane radially, the virtual boundary line is set by corresponding to a corresponding position of the front side surface of the rear vane of the rear working chamber as a radial starting boundary 3411 of the bottom cavity intermittent distribution passage two 82221 of the vane portion, a virtual boundary line is set by displacing a boundary line 341 intersecting the front side surface of the rear vane groove of the rear working chamber and the rotor radially by about 3/4 radial expansion and contraction distances of the vane radially, the virtual boundary line is corresponding to a corresponding position of the front side surface of the rear vane of the rear working chamber as a radial ending boundary 3412 of the bottom cavity intermittent distribution passage two 82221 of the first section of the vane, a second blade part first groove bottom cavity intermittent liquid distribution channel 82221 is arranged in a slotted mode; a boundary line 341 intersected by the front side surface of the blade groove at the rear side of the rear working cavity and the radial outer surface of the rotor is displaced towards the inner diameter by about 3/4 blade radial expansion distance to set a virtual boundary line, the virtual boundary line is corresponding to the corresponding position of the rear side surface of the blade groove at the front side of the rear working cavity and is used as a reference point 3412 of the lower edge of an intermittent liquid distribution channel II 82222 of the bottom cavity of the first type of the groove of the rotor part, a boundary line 341 intersected by the front side surface of the blade groove at the rear side of the rear working cavity and the radial outer surface of the rotor is displaced towards the inner diameter by about 1/4 blade radial expansion distance to set a virtual boundary line, the virtual boundary line is corresponding to the corresponding position of the rear side surface of the blade groove at the front side of the rear working cavity and is used as a datum point 3413 on an intermittent liquid distribution channel II 82222 of the first type groove bottom cavity of the rotor part, a rotor part first-type groove bottom cavity intermittent liquid distribution channel II 82222 is arranged in a hole form and is opened from the front side surface of the rear side blade groove of the rear side working cavity to the corresponding groove bottom cavity; the second blade part first section first type groove bottom cavity intermittent liquid distribution channel 82221 and the second rotor part first type groove bottom cavity intermittent liquid distribution channel 82222 form a second first type groove bottom cavity intermittent liquid distribution channel 8222, wherein the first part is arranged in the rear side working cavity rear side blade, and the second part is arranged in the rotor.
The second type of groove bottom cavity intermittent liquid distribution channel II 8122 is arranged at a position, separated from the hole of the rotor part, of the first type of groove bottom cavity intermittent liquid distribution channel II 8222 in the axial direction of the hole of the rotor part.
This embodiment groove bottom chamber joins in marriage liquid channel structure mainly includes: the blade of the core and the second tank bottom cavity intermittent liquid distribution channel, the first tank bottom cavity intermittent liquid distribution channel and the tank bottom cavity balance liquid distribution channel arranged in the rotor form the clearance channel by the contact working condition of the blade head correction angle and the inner surface of the stator in an action period.
At 244 in fig. 38, the extended discharge port makes the rear correction angle of the blade head and the axial contact line of the stator inner surface to define that the rear part of the blade head contacts the low-pressure working fluid, while the extended injection port, the tank bottom cavity balanced fluid distribution channel 83, the tank bottom cavity balanced fluid distribution channel 84, the first type tank bottom cavity intermittent fluid distribution channel second 8222 and the rear clearance channel 422 (refer to fig. 57 and 58) make the rest of the blade head and the blade tail contact the high-pressure working fluid, and the radial area of the rear part of the blade head is designed according to the hydraulic requirements for keeping the blade in the outward radial expansion tendency; referring to point 247 in fig. 38, the extended outlet makes the front modified angle of the vane head contact the axial line of the stator inner surface to define the front part of the vane head contacting the low pressure working fluid, while the extended inlet, the tank bottom cavity balanced fluid distribution channel 83, the tank bottom cavity balanced fluid distribution channel 84, the second type tank bottom cavity intermittent fluid distribution channel 8122 and the front clearance channel 421 (refer to fig. 59 and 60) make the rest of the vane head and the vane tail contacting the high pressure working fluid, and the radial area of the front part of the vane head is designed according to the hydraulic force requirement for maintaining the vane to be stretched towards the outer diameter. (the radial areas of the rear and front portions of the blade head can be appropriately adjusted according to the experience of a professional engineer.)
Referring to fig. 38 and 39, the main path that the corresponding slot bottom cavity 89 communicates with the front side working cavity or/and the rear side working cavity when the blade head correction angle contacts different circumferential nodes with the inner surface of the stator is shown, and correspondingly, the ratio of the hydraulic force for extending the blade radially outward obtained at the tail part of the blade and the total hydraulic force for retracting the blade radially inward obtained at each part of the blade head is shown:
in operation, as shown in point 241 in fig. 39, the rear working chamber is separated from the discharge port and is not communicated with the extension injection port, the rear working chamber maintains relatively low working fluid pressure, the front working chamber maintains communication with the extension injection port, the corresponding tank bottom chamber is communicated with the second type tank bottom chamber intermittent liquid distribution channel two 8122, the tank bottom chamber balanced liquid distribution channel 83 and the tank bottom chamber balanced liquid distribution channel 84, the blade head middle part and the front clearance channel 421 (see fig. 59 and 60) are communicated with the front working chamber, the blade head middle part is communicated with the corresponding tank bottom chamber through the balanced channel, so that the blade head front part, the blade head middle part and the blade tail part contact high-pressure working fluid P2, and the blade head rear part and the blade tail part contact working fluid with relatively low pressure, as shown in the figure, the hydraulic force for extending the blade to the outer diameter is obtained at the blade tail part and the hydraulic force for retracting the blade to the inner diameter is obtained at the blade head part, the corresponding blade on the bottom cavity of the groove obtains hydraulic force stretching outwards;
at point 242 in fig. 39, the front and rear working chambers are simultaneously communicated with the extension injection port, the corresponding tank bottom chamber is communicated with the front working chamber through the second type of side tank bottom chamber intermittent liquid distribution channel three 8122, the two types of tank bottom chamber intermittent liquid distribution channels start the alternate switching of the respective communication working conditions, the corresponding tank bottom chamber is communicated with the front working chamber through the tank bottom chamber balanced liquid distribution channel 83, the tank bottom chamber balanced liquid distribution channel 84 and the front clearance channel 421 (see fig. 59 and 60), the middle part of the blade head is communicated with the corresponding tank bottom chamber through the balanced channel, so that each part of the blade head and each part of the blade tail contact high-pressure working liquid P2, if the blade tail obtains the hydraulic force for extending the blade to the outer diameter and each part of the blade head obtains the total hydraulic force for retracting the blade to the inner diameter, the blade on the corresponding tank bottom chamber does not obtain the hydraulic force for extending to the outer diameter;
as shown at point 243 of fig. 39, the rear working chamber communicates with the extension injection port, the front working chamber is separated from the inlet port and does not communicate with the extension discharge port, the corresponding tank bottom cavity is communicated with the rear side working cavity through a second 8222 of the first type of tank bottom cavity intermittent liquid distribution channel, the two types of tank bottom cavity intermittent liquid distribution channels complete the alternate switching of the respective communication working conditions, the corresponding tank bottom cavity can also be communicated with the rear side working cavity through a tank bottom cavity balance liquid distribution channel 83, a tank bottom cavity balance liquid distribution channel 84, the middle part of the blade head and a rear side clearance channel 422 (see figures 57 and 58), the middle part of the blade head is communicated with the corresponding tank bottom cavity through the balance channel, thus, all parts of the head part of the blade and the tail part of the blade are contacted with high-pressure working fluid P2, the hydraulic force for expanding the blade outwards and radially obtained by the tail part of the blade as shown in the figure is basically the same as the total hydraulic force for retracting the blade inwards and radially obtained by all parts of the head part of the blade, and the hydraulic force for expanding outwards and radially obtained by the blade on the corresponding groove bottom cavity is basically the same;
at point 244 shown in fig. 38, the rear working chamber is communicated with the extension inlet, the front working chamber is communicated with the extension outlet, the corresponding tank bottom chamber is communicated with the rear working chamber through a second 8222 of the first-type tank bottom chamber intermittent liquid distribution channel, the rear working chamber is communicated with the corresponding tank bottom chamber through a balance channel at the middle part of the blade head of the rear clearance channel 422 (see fig. 57 and 58), so that the rear part of the blade head, the middle part of the blade head and the blade tail are contacted with high-pressure working liquid P2, while the front part of the blade head is contacted with working liquid with relatively high pressure, as shown in the figure, the hydraulic force for extending the blade outwards and radially is greater than the total hydraulic force for retracting the blade inwards and extending the blade on the corresponding tank bottom chamber;
at point 245 shown in fig. 39, the front and rear working chambers are simultaneously communicated with the extended discharge port, the corresponding tank bottom chamber is communicated with the rear working chamber through the second 8222 of the first-type tank bottom chamber intermittent liquid distribution channel, the two-type tank bottom chamber intermittent liquid distribution channels start the respective communication working conditions to be alternately switched again, the corresponding tank bottom cavity is communicated with the rear side working cavity through a tank bottom cavity balance liquid distribution channel 83, a tank bottom cavity balance liquid distribution channel 84, a blade head middle part and a rear side clearance channel 422 (see figures 57 and 58), the blade head middle part is communicated with the corresponding tank bottom cavity through a balance channel, thus, all parts of the head part of the blade and the tail part of the blade are contacted with low-pressure working fluid P1, the hydraulic force for enabling the blade to stretch outwards and radially obtained by the tail part of the blade as shown in the figure is basically the same as the total hydraulic force for enabling the blade to retract inwards and radially obtained by all parts of the head part of the blade, and the hydraulic force for enabling the blade to stretch outwards and radially obtained by the blade on the corresponding groove bottom cavity is not obtained;
at point 246 in fig. 39, the front and rear working chambers are simultaneously communicated with the extended discharge port, the corresponding tank bottom chamber starts to be communicated with the front working chamber through the second type of side tank bottom chamber intermittent liquid distribution channel III 8123, and the two types of tank bottom chamber intermittent liquid distribution channels complete the re-alternating switching of the respective communication working conditions; the corresponding tank bottom cavity is communicated with the rear side working cavity through a tank bottom cavity balance liquid distribution channel 83, a tank bottom cavity balance liquid distribution channel 84, a blade head middle part and a rear side clearance channel 422 (see figures 57 and 58), the blade head middle part is communicated with the corresponding tank bottom cavity through the balance channel, so that each part of the blade head and each part of the blade tail are contacted with low-pressure working liquid P1, the hydraulic force for stretching the blade outwards in the radial direction obtained by the blade tail as shown in the figure is basically the same as the total hydraulic force for retracting the blade inwards obtained by each part of the blade head, and the hydraulic force for stretching outwards in the radial direction is not obtained by the blade on the corresponding tank bottom cavity;
at point 247 in fig. 38, the rear working chamber is kept in communication with the extension outlet, the front working chamber is in communication with the extension inlet, the corresponding bottom chamber is in communication with the front working chamber through the second-type side tank bottom chamber intermittent liquid distribution channel three 8122, the tank bottom chamber balanced liquid distribution channel 83, the tank bottom chamber balanced liquid distribution channel 84, the blade head middle part and the front clearance channel 421 (see fig. 59 and 60), and the blade head middle part is in communication with the corresponding tank bottom chamber through the balanced channel, so that the blade head front part, the blade head middle part and the blade tail part contact the high-pressure working liquid P2, while the blade head rear part contacts the low-pressure working liquid P1, as shown in the figure, the blade tail part obtains a hydraulic force for expanding the blade radially outward which is greater than the total hydraulic force for contracting the blade radially inward contracting of the blade head part, and the blade on the corresponding tank bottom chamber obtains a hydraulic force for expanding the outward radially outward;
and starting when the front side working cavity is separated from the discharge port, entering the next working cycle and repeating.
Referring to fig. 25, 26, 29, 30, 38 and 39, during the whole action cycle, high-pressure working fluid P2 can be obtained when the tank bottom cavity 89 contacts the tank bottom cavity liquid inlet auxiliary channel 96 with the included angle α 4 in the end cover.
Referring to fig. 38 and 39, in the whole action cycle, the intermittent liquid distribution channel structure of the groove bottom cavity enables the corresponding groove bottom cavity to be communicated with at least one corresponding working cavity, and the intermittent liquid distribution channel structure of the groove bottom cavity enables the corresponding groove bottom cavity to continuously obtain optimized liquid distribution with adjustable pressure in sections from the corresponding communicated working cavity; the radial boundary line and the sectional area after the numerical value comparison of the radial telescopic distance of the blades in the intermittent liquid distribution channel of the bottom cavity of the tank is set can be changed and adjusted within a certain range by a person skilled in the art according to the technical requirements, and the specific positions and the sectional areas of other channels in the intermittent liquid distribution channel structure of the bottom cavity of the tank can be changed and adjusted within a certain range; the corresponding tank bottom cavity guides low-pressure working liquid into the cavity through the corresponding working cavity during volume expansion, and the corresponding tank bottom cavity discharges high-pressure working liquid in the cavity to the outside of the motor through the corresponding working cavity during volume reduction; the tank bottom cavity liquid distribution channel structure leads the working liquid flow generated in the process that the corresponding tank bottom cavity works in the volume change to be totally summarized into the theoretical displacement of the motor; thereby increasing the working pressure of the hydraulic vane motor of the present embodiment.
In fig. 38 and 39, the vanes on the corresponding groove bottom cavities mainly utilize the hydraulic force to keep the vanes moving towards the radial direction in the section obtaining the radial extension hydraulic force in the whole action period; the corresponding blade on the bottom cavity of the groove mainly utilizes the centrifugal force generated by the blade in operation and the driving force formed by the corresponding working load preset by a spring in a hydraulic section which is not or basically not stretched out in the radial direction, so that the blade keeps the trend of moving in the radial direction; the working load of the spring can be adjusted more practically and with the experience of a professional engineer.
The structure of the liquid distribution channel of the groove bottom cavity replaces and cancels a liquid distribution channel of higher-pressure working liquid arranged in the left end cover and the right end cover of a vane motor, so that the internal leakage increased in a movement gap between two axial planes of a machine core rotating part and the planes corresponding to the two end covers is partially eliminated.
According to the hydraulic vane motor, the driving force consisting of the liquid distribution channel structure of the groove bottom cavity, the working load preset by the spring and the high-pressure working liquid always distributed at the bottom of the pin is combined, so that at least one side correction angle of each vane head in operation always keeps proper contact stress with the inner surface of the stator, the failure problem caused by abrasion of the inner surface of the stator is improved, and the working pressure of the hydraulic vane motor is improved.
The rest corresponds to example 1.
Example 9: referring to fig. 1, 3 and 24, fig. 41 to 60 show a single-acting hydraulic vane motor according to the present embodiment.
The left and right end covers, stator, rotor and blades in this embodiment are different from embodiment 8 in that:
fig. 41 and 42 show the left end cap 5 adopted in this embodiment, an extended discharge port 93 communicating with the working chamber, an extended injection port 94 communicating with the working chamber, a tank bottom cavity liquid outlet auxiliary channel 95 corresponding to the working chambers on the front and rear sides and simultaneously communicating with the extended discharge port and having an included angle of α 3 in the whole circumferential range, and a tank bottom cavity liquid inlet auxiliary channel 96 corresponding to the working chamber on the smaller side and communicating with the extended injection port and having an included angle of α 4 in the circumferential range, are circumferentially arranged on the end plane corresponding to the stator of the left end cap, the tank bottom cavity liquid outlet auxiliary channel disposes low-pressure working liquid P1 to the communicated tank bottom cavity, and the tank bottom cavity liquid inlet auxiliary channel disposes high-pressure working liquid P2 to the communicated tank bottom cavity.
Fig. 43 and 44 show that in this embodiment, a stator 2 is adopted, which includes an expanding section with an included angle α 5, a reducing section with an included angle α 6, a large circular arc R of a connecting section from the expanding section to the reducing section, and a small circular arc R1 of a connecting section from the reducing section to the expanding section, a liquid outlet matching channel 97 with an included angle α 1 and inclined grooves 972 at front and rear sides is provided from the inner surface to the outer diameter of the stator corresponding to a discharge port 93 extending from an end cap, a liquid inlet matching channel 98 with an included angle α 2 and inclined grooves 982 at front and rear sides is provided from the inner surface to the outer diameter of the stator corresponding to an injection port 94 extending from the end cap, a low-pressure working fluid is configured in the liquid outlet matching channel to the tank bottom cavity balance liquid distribution channel, and a high-pressure working fluid is configured in the liquid outlet matching channel to the tank bottom cavity balance liquid distribution channel. (the angles of α 1 and α 2 and the angles of α 5 and α 6 are designed according to actual conditions)
See fig. 45 and 56, which are the right end cap 5-1 adopted in the present embodiment, the right end cap and the left end cap are correspondingly provided with: an extended discharge port 93, an extended filling port blind groove 941, a groove bottom cavity liquid outlet auxiliary channel 95 and a groove bottom cavity liquid inlet auxiliary channel blind groove 961.
See fig. 52 and 53 for the rotor 3 of the present embodiment, the rotor outer diameter R2, 9 blade grooves 31 with a radial tilt angle of 5 degrees in the radial direction theta set in fig. 52 with respect to the radial direction and the working direction in the rotor,
fig. 47 to 51 show a vane of this embodiment, in which the vane is disposed in a vane slot of a rotor and has the same inclination angle as the vane slot of the rotor, a difference value obtained by subtracting one half of the telescopic distance of the vane from the larger radius of the inner surface of the stator and the axis of the rotor is taken as a radius and the axis of the rotor is taken as a circle center, the vane of this embodiment adopts a virtual circle whose head can be simultaneously contacted with the virtual circle as required to correspondingly set front and rear side correction angles, a middle part of the vane head is formed between the respective top ends of the front and rear side correction angles, and when the one side correction angle of the extended vane is separated from the inner surface of the stator, a working chamber on the side adjacent to the side correction angle of the vane and the middle part of the vane head of the vane form the side gap channel;
the arrangement of the tank bottom cavity balance liquid distribution channel: two groove bottom cavity balance liquid distribution channels 83 axially distributed from the inner diameter in the middle part of the head part of the blade are arranged in the blade; the radial position of the corresponding blade is on the maximum position, a tank bottom cavity balance liquid distribution channel 84 is axially arranged in the center, a blade part tank bottom cavity balance liquid distribution channel 841 and a rotor part tank bottom cavity balance liquid distribution channel 842 form a tank bottom cavity balance liquid distribution channel 84, the blade part 841 firstly forms a blind hole in the middle part of the head part of the blade towards the tail part of the blade and then forms a hole on the rear side surface of the blade to communicate the blind hole, the radial lower edge of the hole on the rear side surface of the blade reaches the boundary line of the intersection of the front side surface of the rotor blade groove and the circular arc surface at the bottom of the rotor blade groove, which is about 2/3 the radial expansion distance of the blade, the rear side surface of the rotor blade groove is provided with the rotor part tank bottom cavity balance liquid distribution channel 842 in a slotted mode, the boundary line of the intersection of the rear side surface of the rotor blade groove and the circular arc surface at the bottom of the rotor blade groove is about 1 radial expansion distance of the blade, and the front surface of the corresponding rotor blade groove is used as the radial starting boundary line of the rotor part tank bottom cavity balance liquid distribution channel 842, the rotor part tank bottom cavity balance liquid distribution channel 842 is opened to a corresponding tank bottom cavity in the inner diameter direction (the tank bottom cavity balance liquid distribution channel increases or decreases the number of holes according to the experience of professional engineers);
the two radial tail ends of the tank bottom cavity balance liquid distribution channel 83 are expanded with spring holes 61, and springs 6 are arranged in the spring holes (see fig. 54).
The small stator circular arc R1 is larger than the rotor outer diameter R2.
In the embodiment shown in fig. 56, for any vane located at the maximum radial position and having the rear working chamber communicated with the extension inlet and the front working chamber communicated with the extension outlet, the radial inclination angle defined by the vane slot of the rotor to the vane is mainly used to determine that the front correction angle of the vane contacts with the inner surface of the stator, and a rear clearance channel 422 is formed between the middle part of the vane head and the rear working chamber, as shown in enlarged views 57 and 58; the rear correcting angle of the blade is mainly determined by the radial inclination angle of the rotor blade groove to the blade, and is contacted with the inner surface of the stator, and a front clearance channel 421 is formed between the middle part of the head of the blade and the front working cavity, namely enlarged images 59 and 60.
See fig. 47-56 in this embodiment, two types of tank bottom cavity intermittent liquid distribution channels are adopted in the matching group: a second type tank bottom cavity intermittent liquid distribution channel III 8124 which is partially arranged in the front side blade of the front side working cavity and partially arranged in the rotor is axially arranged in the center between the corresponding front side working cavity and the corresponding tank bottom cavity, and a first type tank bottom cavity intermittent liquid distribution channel III 8224 which is partially arranged in the rear side blade of the rear side working cavity and partially arranged in the rotor is axially arranged in the center between the corresponding rear side working cavity and the corresponding tank bottom cavity.
See fig. 56, the carrier blade is set at the maximum radial position, when the carrier blade is used as the front blade of the front working chamber, the third 8124 of the second type of tank bottom chamber intermittent liquid distribution channel is set, when the carrier blade is used as the back blade of the back working chamber and when the carrier blade is used as the corresponding blade of the back working chamber, the third 8224 of the first type of tank bottom chamber intermittent liquid distribution channel is set:
when the vane shown in fig. 56 is used as the front vane of the front working chamber, a virtual boundary line is set at the value that the second boundary line 342 where the rear side surface of the front vane groove of the front working chamber and the radial outer surface of the rotor intersect is displaced outwards by about 3/10 vane radial expansion and contraction distances, and the virtual boundary line is corresponding to the corresponding position of the rear side surface of the front vane of the front working chamber and is used as the radial starting boundary 3421 of the second type groove bottom chamber intermittent liquid distribution passage three 81241 of the vane part and opens the vane head part outwards in a slotted mode; a virtual boundary line is set at the value of 1/5 blade radial expansion and contraction distance of a second boundary line 342 intersected by the rear side surface of the front side blade groove of the front side working cavity and the radial outer surface of the rotor, the virtual boundary line is corresponding to the corresponding position of the rear side surface of the front side blade groove of the front side working cavity to be used as a radial starting boundary 3422 of a third 81242 platform of the second type groove bottom cavity intermittent liquid distribution channel, a virtual boundary line is set at the value of 19/20 blade radial expansion and contraction distance of the second boundary line 342 intersected by the rear side surface of the front side blade groove of the front side working cavity and the radial outer surface of the rotor to be used as a radial ending boundary 3423 of the third 81242 platform of the second type groove bottom cavity intermittent liquid distribution channel, holes of the third 81242 of the second type groove bottom cavity intermittent liquid distribution channel are arranged in a hole opening mode, the hole is opened from the platform to the corresponding tank bottom cavity, and the platform and the hole form a rotor part second-type tank bottom cavity intermittent liquid distribution channel III 81242; the vane part second type groove bottom cavity intermittent liquid distribution channel III 81241 and the rotor part second type groove bottom cavity intermittent liquid distribution channel III 81242 form a second type groove bottom cavity intermittent liquid distribution channel III 8124, wherein the vane part is arranged in the front side vane of the front side working cavity, and the rotor part is arranged in the rotor.
And a third 8224 intermittent liquid distribution channel of the first groove bottom cavity is arranged: when the vane shown in fig. 56 is used as the rear vane of the rear working chamber, a virtual boundary line is set by a value of about 1/2 radial expansion and contraction distances of the vane from the first boundary line 341 where the front side surface of the rear vane groove of the rear working chamber intersects with the radial outer surface of the rotor, the virtual boundary line is set to a corresponding position of the front side surface of the rear vane of the rear working chamber as the radial starting boundary 3411 of the first kind of groove bottom cavity intermittent liquid distribution passage three 82241 of the vane portion, the first boundary line 341 where the front side surface of the rear vane groove of the rear working chamber intersects with the radial outer surface of the rotor is set to a value of about 7/10 radial expansion and contraction distances of the vane, the virtual boundary line is set to a corresponding position of the front side surface of the rear vane of the rear working chamber as the radial ending boundary 3412 of the first kind of groove bottom cavity intermittent liquid distribution passage three 82241 of the vane portion, an intermittent liquid distribution channel III 82241 of a first groove bottom cavity of the blade part is arranged in a slotted mode; a boundary line 341 intersecting the front side surface of the blade groove at the rear side of the rear side working cavity and the radial outer surface of the rotor is radially displaced by about 1/5 to set a virtual boundary line, the virtual boundary line is corresponding to the corresponding position of the front side surface of the blade groove at the rear side of the rear side working cavity and is used as a radial starting boundary 3413 of a third 82242 intermittent liquid distribution channel of the bottom cavity of the first type of the groove of the rotor part, a first boundary line 341 intersecting the front side surface of the blade groove at the rear side of the rear working cavity and the radial outer surface of the rotor is radially displaced by about 7/10 to set a virtual boundary line, the virtual boundary line is corresponding to the corresponding position of the front side surface of the blade groove at the rear side of the rear working cavity and is used as a radial termination boundary 3412 of the intermittent liquid distribution channel III 82242 of the first type slot bottom cavity of the rotor part, an intermittent liquid distribution channel III 82242 of a first type of groove bottom cavity of the rotor part is arranged in a form of an opening and is opened from the front side surface of the blade groove at the rear side of the rear side working cavity to the corresponding groove bottom cavity; the first type groove bottom cavity intermittent liquid distribution channel III 82241 of the blade part and the first type groove bottom cavity intermittent liquid distribution channel III 82242 of the rotor part form a first type groove bottom cavity intermittent liquid distribution channel III 8224, wherein the blade part is arranged in the middle of the rear side working cavity and corresponds to the rotor part in the blade, and the rotor part is arranged in the rotor.
The third 8124 of the second type of groove bottom cavity intermittent liquid distribution channel is arranged at a position separated from the third 8224 of the first type of groove bottom cavity intermittent liquid distribution channel in the axial direction of the hole of the rotor part.
The liquid passageway major structure is joined in marriage to this embodiment groove bottom chamber includes: the blade of the core and the second tank bottom cavity intermittent liquid distribution channel, the first tank bottom cavity intermittent liquid distribution channel and the tank bottom cavity balance liquid distribution channel arranged in the rotor form the clearance channel by the contact working condition of the blade head correction angle and the inner surface of the stator in an action period.
At 244 in fig. 55, the extension discharge port makes the rear correction angle of the blade head and the axial contact line of the stator inner surface to define that the rear part of the blade head contacts the low-pressure working fluid, while the extension injection port, the tank bottom cavity balance fluid distribution channel 83, the tank bottom cavity balance fluid distribution channel 84, the first type tank bottom cavity intermittent fluid distribution channel three 8224 and the rear clearance channel 422 (refer to fig. 57 and 58) make the rest of the blade head and the blade tail contact the high-pressure working fluid, and the radial area of the rear part of the blade head is designed according to the hydraulic requirement for keeping the blade in the outward radial expansion tendency; referring to fig. 54 at point 247, the extension outlet divides the axial contact line between the front modified angle of the vane head and the inner surface of the stator to make the front part of the vane head contact the low pressure working fluid, while the extension inlet, the tank bottom cavity balance fluid distribution channel 83, the tank bottom cavity balance fluid distribution channel 84, the second type tank bottom cavity intermittent fluid distribution channel three 8124 and the front clearance channel 421 (refer to fig. 59 and 60) make the rest of the vane head and the vane tail contact the high pressure working fluid, and the radial area of the front part of the vane head is designed according to the hydraulic requirements for maintaining the vane in a tendency of expanding to the outer diameter. (the radial areas of the rear and front portions of the blade head can be appropriately adjusted according to the experience of a professional engineer.)
Referring to fig. 54 and 55, the main path that the corresponding slot bottom cavity 89 communicates with the front side working cavity or/and the rear side working cavity when the blade head correction angle contacts different circumferential nodes with the inner surface of the stator is shown, and correspondingly, the ratio of the hydraulic force for extending the blade radially outward obtained at the tail part of the blade and the total hydraulic force for retracting the blade radially inward obtained at each part of the blade head is shown:
in operation, as shown at point 241 in fig. 55, the rear working chamber is disconnected from the drain port and is not in communication with the extension injection port, the rear working chamber maintains a relatively low working fluid pressure, the front working chamber maintains communication with the extension injection port, the corresponding tank bottom cavity is communicated with the front side working cavity through a second type tank bottom cavity intermittent liquid distribution channel III 8124, a tank bottom cavity balance liquid distribution channel 83, a tank bottom cavity balance liquid distribution channel 84, the middle part of the blade head and the front side clearance channel 421, the middle part of the blade head is communicated with the corresponding tank bottom cavity through a balance channel, so that the front part of the blade head, the middle part of the blade head and the tail part of the blade contact the high-pressure working fluid P2, the rear part of the head of the blade is contacted with working fluid with relatively low pressure, as shown in the figure, the hydraulic force for enabling the blade to stretch outwards and radially obtained by the tail of the blade is greater than the total hydraulic force for enabling the blade to retract towards the inner diameter obtained by each part of the head of the blade, and the hydraulic force for enabling the blade on the corresponding groove bottom cavity to stretch outwards and radially obtained by the blade on the corresponding groove bottom cavity;
at point 242 in fig. 55, the front and rear working cavities are simultaneously communicated with the extension injection port, the corresponding tank bottom cavity is communicated with the front working cavity through the second tank bottom cavity intermittent liquid distribution channel III 8124, the two tank bottom cavity intermittent liquid distribution channels start the alternate switching of the respective communication working conditions, the corresponding tank bottom cavity is communicated with the front working cavity through the tank bottom cavity balanced liquid distribution channel 83, the tank bottom cavity balanced liquid distribution channel 84, the middle part of the blade head and the front clearance channel 421, and the middle part of the blade head is communicated with the corresponding tank bottom cavity through the balanced channel, so that each part of the blade head and each part of the blade tail are contacted with high-pressure working liquid P2, the hydraulic force for expanding the blade towards the outer diameter is basically the same as the total hydraulic force for retracting the blade towards the inner diameter is obtained by each part of the blade head as shown in the figure, and the blade on the corresponding tank bottom cavity does not obtain the hydraulic force for expanding towards the outer diameter;
at point 243 in fig. 54, the rear working chamber communicates with the extension inlet, the front working chamber is separated from the inlet and is not communicated with the extension outlet, the front working chamber maintains relatively high working fluid pressure, the corresponding tank bottom chamber communicates with the rear working chamber through the tank bottom chamber balance fluid distribution channel 83, the tank bottom chamber balance fluid distribution channel 84, the blade head middle part and the rear clearance channel 422, the blade head middle part communicates with the corresponding tank bottom chamber through the balance channel, so that the blade head rear part, the blade head middle part and the blade tail part contact high-pressure working fluid P2, and the blade head front part contacts relatively high-pressure working fluid, as shown in the figure, the blade tail part obtains the hydraulic force for extending the blade outward radially which is greater than the total hydraulic force for retracting the blade inward radially which is obtained by the blade head part, and the blade on the corresponding tank bottom chamber obtains the hydraulic force for extending outward radially;
at 244 of fig. 55, the rear working chamber is communicated with the extension inlet, the front working chamber is communicated with the extension outlet, the corresponding tank bottom chamber is communicated with the rear working chamber through the first tank bottom chamber intermittent liquid distribution channel III 8224, the two tank bottom chamber intermittent liquid distribution channels are alternately switched in respective communication working conditions, the corresponding tank bottom chamber is communicated with the rear working chamber through the tank bottom chamber balanced liquid distribution channel 83, the tank bottom chamber balanced liquid distribution channel 84, the blade head middle part and the rear clearance channel 422 as shown in fig. 56, the blade head middle part is communicated with the corresponding tank bottom chamber through the balanced channel, so that the blade head rear part, the blade head middle part and the blade tail part are contacted with high-pressure working liquid P2, and the blade head front part is contacted with low-pressure working liquid P1, as shown in the figure, the blade tail part obtains the hydraulic force for stretching the blade to the outer diameter which is greater than the total hydraulic force for retracting the blade head part to the inner diameter, the corresponding blade on the bottom cavity of the groove obtains hydraulic force stretching outwards;
at 245 in FIG. 55, the front and rear working chambers are simultaneously connected with the extended outlets, the corresponding tank bottom chamber is kept connected with the rear working chamber through a first type tank bottom chamber intermittent liquid distribution channel III 8224, the corresponding tank bottom chamber starts to be connected with the front working chamber through a second type tank bottom chamber intermittent liquid distribution channel III 8124, the two types of tank bottom chamber intermittent liquid distribution channels start to be respectively and alternately switched in the connection working condition, the corresponding tank bottom chamber can also be connected with the rear working chamber through a tank bottom chamber balanced liquid distribution channel 83, a tank bottom chamber balanced liquid distribution channel 84, a blade head middle part and a rear clearance channel 422, the blade head middle part is connected with the corresponding tank bottom chamber through a balanced channel, so that the blade head parts and the blade tail part are contacted with low-pressure working liquid P1, the blade tail part obtains the hydraulic force for extending the blade to the outer diameter and the blade head parts obtain the total hydraulic force for retracting the blade to the inner diameter basically the same as the blade head part, the blades on the corresponding groove bottom cavity do not obtain hydraulic force stretching outwards;
at point 246 in fig. 55, the front and rear working cavities are simultaneously communicated with the extended discharge port, the corresponding tank bottom cavity is kept communicated with the front working cavity through the third second-type tank bottom cavity intermittent liquid distribution channel 8124, the corresponding tank bottom cavity is communicated with the rear working cavity through the third first-type tank bottom cavity intermittent liquid distribution channel 8224, and the two types of tank bottom cavity intermittent liquid distribution channels complete the alternate switching of the respective communication working conditions; the corresponding tank bottom cavity can be communicated with the rear side working cavity through a tank bottom cavity balance liquid distribution channel 83, a tank bottom cavity balance liquid distribution channel 84, a blade head middle part and a rear side clearance channel 422, the blade head middle part is communicated with the corresponding tank bottom cavity through the balance channel, so that each part of the blade head and each part of the blade tail are contacted with low-pressure working liquid P1, the hydraulic force for stretching the blade outwards in the radial direction obtained by the blade tail as shown in the figure is basically the same as the total hydraulic force for retracting the blade inwards by each part of the blade head, and the hydraulic force for stretching outwards in the radial direction obtained by the blade on the corresponding tank bottom cavity is not obtained by the blade on the corresponding tank bottom cavity;
at point 247 in fig. 54, the rear working chamber is communicated with the extension outlet, the front working chamber is communicated with the extension inlet, the corresponding tank bottom chamber is communicated with the front working chamber through the second tank bottom chamber intermittent liquid distribution channel three 8124, the tank bottom chamber balanced liquid distribution channel 83, the tank bottom chamber balanced liquid distribution channel 84, the blade head middle part and the front clearance channel 421, the blade head middle part is communicated with the corresponding tank bottom chamber through the balanced channel, so that the blade head front part, the blade head middle part and the blade tail part are contacted with high-pressure working liquid P2, and the blade head rear part is contacted with low-pressure working liquid P1, as shown in the figure, the blade tail part obtains the hydraulic force for extending the blade outward radial direction which is greater than the total hydraulic force for retracting the blade inward radial direction obtained by the blade head part, and the blade on the corresponding tank bottom chamber obtains the hydraulic force for extending the outward radial direction;
and starting when the front side working cavity is separated from the discharge port, entering the next working cycle and repeating.
Referring to fig. 41, 42, 45, 54 and 55, in the whole action period, when the groove bottom cavity 89 contacts the groove bottom cavity liquid outlet auxiliary channel 95 with the included angle of α 3 in the end cover, the channel sectional area of the discharged low-pressure working liquid P1 can be increased, and when the groove bottom cavity 89 contacts the groove bottom cavity liquid inlet auxiliary channel 96 with the included angle of α 4 in the end cover, the high-pressure working liquid P2 can be obtained.
The rest corresponds to the description in example 8.
Example 10: the embodiment is a through shaft multiple double-acting hydraulic vane motor, and the difference from the embodiment 1 is that, referring to fig. 61 and fig. 23: a movement with the same working direction and different displacement as the working direction of the embodiment 1 and an intermediate end cover 5-2 are added, and whether each movement works or not is regulated and controlled by the prior art.
The rest corresponds to those described in example 1.
Example 11: the embodiment is a through-shaft multiple double-acting hydraulic vane motor, and is different from the embodiment 1 with reference to fig. 61 and fig. 1 to 23: a movement with the same working direction and the same displacement as the working direction of the embodiment 1 and an intermediate end cover 5-2 are added, and whether each movement works or not is regulated and controlled by the prior art.
The rest corresponds to that described in example 1.
Example 12: the embodiment is a through-shaft multiple double-acting hydraulic vane motor, and is different from the embodiment 1 with reference to fig. 61 and fig. 1 to 23: a movement with different working directions and same displacement and a middle end cover 5-2 are added, and whether each movement works or not is regulated and controlled by the prior art.
The rest corresponds to that described in example 1.
Example 13: the embodiment is a through-shaft multiple double-acting hydraulic vane motor, and is different from the embodiment 1 with reference to fig. 61 and fig. 1 to 23: a movement with different displacement and different working directions from the embodiment 1 and an intermediate end cover 5-2 are added, and whether each movement works or not is regulated and controlled by the prior art.
The rest corresponds to that described in example 1.
The number of the rotor blade grooves and blades, the number and the positions of the springs and the pins, the number and the positions of the balance liquid distribution channels, the action period contained in one working rotation of the rotor and the number, the positions and the sectional areas of the intermittent liquid distribution channels of the bottom cavity of each groove can be adjusted according to the actual number by a person skilled in the art.
The above examples are intended to illustrate the invention, but not to limit it.
Claims (13)
1. A cartridge for a hydraulic vane motor, comprising: the rotor comprises a stator, a rotor, blades, a left end cover and a right end cover; the surface of the inner cavity of the stator comprises one group or a plurality of groups of two variable-diameter sections which are circumferentially changed from the axis of the movement and are not connected with each other, the rotor is provided with a plurality of rotor blade grooves and can be rotatably arranged in the inner cavity of the stator, the blades can be telescopically arranged in each rotor blade groove, a spring which enables a mother blade to have the outward radial stretching tendency is arranged between each blade and the rotor, and the left end cover and the right end cover are respectively positioned at two axial ends of the stator; the rotor and the blades mainly form a rotating part in the machine core;
a working cavity is correspondingly formed between two adjacent and extended blades, the rotor, the stator and the two end covers; a groove bottom cavity is correspondingly formed among the blade, the rotor blade groove and the two end covers;
the core of the hydraulic vane motor is arranged in the inner cavity of the motor shell with an injection port for injecting high-pressure working fluid and a discharge port for discharging low-pressure working fluid; the core of hydraulic vane motor is provided with the extension filling opening and extends the let-off including being equipped with: the injection port can be communicated with the working cavity in contact with one of the reducing sections by adopting an extension injection port, the discharge port can be communicated with the working cavity in contact with the other reducing section by adopting an extension discharge port, and the extension injection port and the extension discharge port are circumferentially arranged in a separated manner and cannot be communicated with the same working cavity at the same time; the diameter-changing section of the inner surface of the stator corresponding to the extension injection port is an expanding section, and the diameter-changing section corresponding to the extension discharge port is a reducing section;
the core of the hydraulic vane motor is a mechanism for converting pressure energy of high-pressure working fluid in a working cavity communicated with the extending injection port into mechanical energy for driving the rotor to rotate, two adjacent working cavities corresponding to the same vane are simultaneously positioned in the working of the diameter expanding section, and the rotor rotates towards the working cavity with larger volume; a transmission shaft penetrates through the core of the hydraulic vane motor, and a rotor in the core drives the transmission shaft to work;
the volume of the working cavity is periodically and correspondingly changed along with the radial displacement of the corresponding blade in the rotary displacement, the working cavity which is communicated with the extension injection port and is in contact with the inner surface diameter expansion section of the stator is injected into the working cavity by high-pressure working liquid when the volume is increased, and the working cavity which is communicated with the extension discharge port and is in contact with the inner surface diameter reduction section of the stator is discharged out of the working cavity when the volume is decreased; so that the working fluid pressure in each working chamber has the characteristic of section-wise change;
the method is characterized in that:
the head of the blade is at least provided with a front correction angle and a rear correction angle which can simultaneously contact the inner surface of the stator in the direction corresponding to the rotation direction of the rotor, and the middle part of the head of the blade is formed between the top ends of the front correction angle and the rear correction angle;
a tank bottom cavity balance liquid distribution channel is arranged in the rotating part and is used for enabling the corresponding tank bottom cavity where the blade is located to be communicated with the middle part of the head of the blade all the time;
in the working period, when a side correcting angle of the extending blade is separated from the inner surface of the stator, the side clearance channel is formed between the side working cavity adjacent to the side correcting angle in the blade and the middle part of the blade head of the blade; in the process that the volumes of the front working cavity and the rear working cavity are simultaneously increased, the corresponding tank bottom cavity is communicated with the front working cavity through the corresponding balance liquid distribution channel, the middle part of the blade head and the front clearance channel;
the rotary part is provided with a groove bottom cavity intermittent liquid distribution channel which is used for enabling the groove bottom cavity corresponding to the blade to be intermittently communicated with the front side working cavity and the rear side working cavity;
in the working process that at least the volumes of the working cavities on the front side and the rear side of the blade are increased at the same time, the corresponding tank bottom cavity is switched from the working cavity communicated with the front side through the tank bottom cavity intermittent liquid distribution channel to the working cavity communicated with the rear side through the tank bottom cavity intermittent liquid distribution channel, and at least in the working process that the volumes of the working cavities on the front side and the rear side of the blade are decreased at the same time, the corresponding tank bottom cavity is switched from the working cavity communicated with the rear side through the tank bottom cavity intermittent liquid distribution channel to the working cavity communicated with the front side through the tank bottom cavity intermittent liquid distribution channel;
each tank bottom cavity is provided with a tank bottom cavity auxiliary liquid distribution channel and a tank bottom cavity intermittent liquid distribution channel which correspond to each other;
in the action period work, the bottom cavities of the grooves can obtain segmental change of the working fluid pressure in the respective cavities from the correspondingly communicated working cavities under the mutual matching of the corresponding clearance channels, the bottom cavity balance fluid distribution channels and the bottom cavity intermittent fluid distribution channels, so that the contact stress formed by the hydraulic force of the head parts of the blades and the inner surface of the stator of the extension injection inlet section is adjusted and improved.
2. The hydraulic vane pump cartridge of claim 1, wherein: the blade is designed correspondingly according to the hydraulic force which is required to lead the blade to keep the outward diameter stretching trend and tends to the outward diameter, aiming at the working condition that the extending discharge port leads the rear part of the head part of the blade divided by the rear side correction angle of the blade and the axial contact line of the inner surface of the stator to contact low-pressure working fluid, and the extending injection port and the tank bottom cavity balance liquid distribution channel lead the rest part of the head part of the blade and the tail part of the blade to contact high-pressure working fluid; the radial area of the front part of the blade head is correspondingly designed according to the hydraulic force which is required to lead the blade to keep the outward diameter expansion trend and tends to the outward diameter.
3. The movement of a hydraulic vane motor according to claim 1, characterized in that: the tank bottom cavity intermittent liquid distribution channel is divided into a first type tank bottom cavity intermittent liquid distribution channel and a second type tank bottom cavity intermittent liquid distribution channel: the first type of tank bottom cavity intermittent liquid distribution channel is respectively arranged between the rear side working cavity and the corresponding tank bottom cavity and is used for enabling the corresponding tank bottom cavity to be intermittently communicated with the rear side working cavity during working, and the second type of tank bottom cavity intermittent liquid distribution channel is respectively arranged between the front side working cavity and the corresponding tank bottom cavity and is used for enabling the corresponding tank bottom cavity to be intermittently communicated with the front side working cavity during working;
the blade is positioned on the circumferential position of the inner surface of the stator, the respective volume sizes of the front and rear side working cavities of the blade are controlled, in an action period, the first type of tank bottom cavity intermittent liquid distribution channel enables the rear side working cavity with relatively large volume and maximum volume to be communicated with the corresponding tank bottom cavity, and the second type of tank bottom cavity intermittent liquid distribution channel enables the front side working cavity with relatively small volume and minimum volume to be communicated with the corresponding tank bottom cavity; the first type of tank bottom cavity intermittent liquid distribution channel enables the communication working condition of the rear side working cavity and the corresponding tank bottom cavity to be alternately switched and then switched with the communication working condition of the second type of tank bottom cavity intermittent liquid distribution channel enables the front side working cavity and the corresponding tank bottom cavity to be switched in one of the following three modes:
the first mode is as follows: the switching is arranged in the process that the working cavities on the front side and the rear side are simultaneously enlarged, when the corresponding tank bottom cavity is communicated with the rear working cavity which is connected with the extension injection port and has the enlarged volume through the first-class tank bottom cavity intermittent liquid distribution channel, the switching is started, when the corresponding groove bottom cavity is communicated with the front side working cavity which is connected with the extension injection port and has larger volume through the second type groove bottom cavity intermittent liquid distribution channel, the switching is completed, the re-switching can be arranged in the process from the rear side working position to the front side working position, when the corresponding tank bottom cavity is communicated with the front side working cavity which is connected with the extension discharge port and has a reduced volume through the intermittent liquid distribution channel of the second tank bottom cavity, the switching is started, when the corresponding tank bottom cavity is communicated with the rear side working cavity which is connected with the extension discharge port and has a reduced volume through the first type of tank bottom cavity intermittent liquid distribution channel, the switching is completed;
the second way is: the switching is at least arranged in the process that the front side working cavity and the rear side working cavity are simultaneously enlarged, the switching is started when the corresponding tank bottom cavity is communicated with the front side working cavity which is connected with the extension injection port through the second type tank bottom cavity intermittent liquid distribution channel and the volume of which is enlarged, the switching is completed when the corresponding tank bottom cavity starts to be communicated with the rear side working cavity which is connected with the extension injection port through the first type tank bottom cavity intermittent liquid distribution channel and the volume of which is enlarged, the switching is arranged in the process that the front side working cavity and the rear side working cavity are simultaneously reduced, the switching is started when the corresponding tank bottom cavity is communicated with the rear side working cavity which is connected with the extension discharge port through the first type tank bottom cavity intermittent liquid distribution channel and the volume of which is reduced, and the switching is completed when the corresponding tank bottom cavity starts to be communicated with the front side working cavity which is connected with the extension discharge port through the second type tank bottom cavity intermittent liquid distribution channel and the volume of which is reduced;
or the third mode is as follows: the switching is at least arranged in the process that the working cavities on the front side and the rear side are simultaneously enlarged, when the corresponding tank bottom cavity is communicated with the front working cavity which is connected with the extension injection port through the second type of tank bottom cavity intermittent liquid distribution channel and has enlarged volume, the switching is started, when the corresponding groove bottom cavity is communicated with the rear side working cavity which is connected with the extending injection port and has a larger volume through the first type groove bottom cavity intermittent liquid distribution channel, the switching is completed, the re-switching can be arranged in the process from the rear side working and separating from the extension injection port to the front side working cavity communicated with the extension injection port, when the corresponding tank bottom cavity is communicated with the front side working cavity which is connected with the extension outlet and has a reduced volume through the second type of tank bottom cavity intermittent liquid distribution channel, the switching is started again, when the corresponding tank bottom cavity is communicated with the rear side working cavity which is connected with the extension discharge port and has a reduced volume through the first type tank bottom cavity intermittent liquid distribution channel, the switching is completed.
4. A movement for a hydraulic vane motor according to claim 3, characterized in that: the rotor blade groove is provided with a selected radial inclination angle corresponding to the rotation direction of the rotor within the range of 0-5 degrees; when the inclination angle of the rotor blade slot is such that the middle part of the blade head of the blade on the corresponding slot bottom cavity has a process of communicating the same extension injection port through the front side clearance channel and the front side working cavity and then through the rear side clearance channel and the rear side working cavity, the second mode adopted for the alternating switching and the switching again can be set in the process, or the third mode adopted for the alternating switching and the switching again can be set.
5. A movement for a hydraulic vane motor according to claim 3, characterized in that: the first type of groove bottom cavity intermittent liquid distribution channel is arranged in a corresponding part of a blade at the front side of the rear side working cavity, and the communication and disconnection between the corresponding groove bottom cavity and the rear side working cavity are regulated and controlled by the radial displacement of the blade; or the first groove bottom cavity intermittent liquid distribution channel part is arranged in a corresponding part of the blade with a contact surface with the rear side working cavity, and the first groove bottom cavity intermittent liquid distribution channel part is partially arranged in a corresponding part of the rotor and can be mutually matched and communicated, and the communication and disconnection between the corresponding groove bottom cavity and the rear side working cavity are regulated and controlled by the radial displacement of the corresponding blade;
the intermittent liquid distribution of the second groove bottom cavity is arranged in the corresponding part of the rear blade of the front side working cavity, and the communication and disconnection between the corresponding groove bottom cavity and the front side working cavity are regulated and controlled by the radial displacement of the blade; or the intermittent liquid distribution channel part of the groove bottom cavity of the second type is arranged in a corresponding part of the blade with a contact surface with the front side working cavity, and the intermittent liquid distribution channel part is partially arranged in a corresponding part of the rotor and can be mutually matched and communicated, and the communication and disconnection between the corresponding groove bottom cavity and the front side working cavity are regulated and controlled by the radial displacement of the corresponding blade;
and intermittent liquid distribution channels of a first type and a second type of groove bottom cavities adopting a third switching and re-switching mode are respectively arranged in corresponding parts of at least two blades and corresponding parts of the rotor.
6. The movement of a hydraulic vane motor according to claim 1, characterized in that: the blade is provided with a first end penetrating through the middle part of the head of the blade, and a second end penetrating through the tail of the blade is communicated with a corresponding tank bottom cavity balance liquid distribution channel; or the blade and the rotor are provided with a groove bottom cavity balance liquid distribution channel, wherein the first end of the groove bottom cavity balance liquid distribution channel penetrates through the middle part of the head of the blade, and the second end of the groove bottom cavity balance liquid distribution channel penetrates through the side wall of the blade and can be communicated with the corresponding groove bottom cavity through a groove in the rotor all the time.
7. The movement of a hydraulic vane motor according to claim 6, characterized in that: the middle part of the blade head is provided with a groove which can still form the middle part of the blade head and is penetrated by the first end in the groove bottom cavity balance liquid distribution channel.
8. The movement of a hydraulic vane motor according to claim 1, characterized in that: the extended injection port is disposed in at least one end cap and/or stator; the extended discharge openings are provided in the left and right end caps and/or the stator.
9. The movement of a hydraulic vane motor according to claim 1, characterized in that: the stator is provided with a liquid inlet matching channel corresponding to the middle part of the blade head in the range of the front and rear working cavities communicated with the extension filling opening at the same time and/or a liquid outlet matching channel corresponding to the middle part of the blade head in the range of the front and rear working cavities communicated with the extension discharging opening at the same time.
10. The movement of a hydraulic vane motor according to claim 9, characterized in that: the stator is provided with a liquid inlet direct connection channel which enables the liquid inlet matching channel to become an extension filling opening or/and a liquid outlet direct connection channel which enables the liquid outlet matching channel to become an extension discharging opening.
11. A hydraulic vane motor, comprising: a hydraulic vane motor incorporating a hydraulic vane motor cartridge as claimed in any one of claims 1 to 10.
12. The hydraulic vane motor of claim 11, wherein: the hydraulic vane motor is internally provided with a plurality of hydraulic vane motor cores with the same working direction, different displacements, different working directions or different displacements.
13. A hydraulic drive system includes an actuator; the method is characterized in that: a hydraulic vane motor as claimed in any one of claims 11 or 12 incorporated into the actuator.
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| CN202110257792.0A CN115076022A (en) | 2021-03-10 | 2021-03-10 | Core of hydraulic vane motor, hydraulic vane motor and hydraulic transmission system |
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| CN202110257792.0A CN115076022A (en) | 2021-03-10 | 2021-03-10 | Core of hydraulic vane motor, hydraulic vane motor and hydraulic transmission system |
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| CN115076022A true CN115076022A (en) | 2022-09-20 |
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| CN202110257792.0A Pending CN115076022A (en) | 2021-03-10 | 2021-03-10 | Core of hydraulic vane motor, hydraulic vane motor and hydraulic transmission system |
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| Country | Link |
|---|---|
| CN (1) | CN115076022A (en) |
-
2021
- 2021-03-10 CN CN202110257792.0A patent/CN115076022A/en active Pending
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