CN115370568A

CN115370568A - Rotor blade assembly and hydraulic vane pump

Info

Publication number: CN115370568A
Application number: CN202110545110.6A
Authority: CN
Inventors: 肖雷明
Original assignee: Individual
Current assignee: Individual
Priority date: 2021-05-19
Filing date: 2021-05-19
Publication date: 2022-11-22

Abstract

The invention relates to the technical field of hydraulic vane pumps, and discloses a rotor blade assembly and a hydraulic vane pump with the same: the front and back matching surfaces of the vane side surface and the vane groove side surface at the minimum and maximum radial positions are respectively provided with a front and back balancing chambers which are communicated with each other and a front and back binding surface which are respectively corresponding to the vane side surface and/or the vane groove side surface; according to the requirement that the blades are always kept in contact with the inner surface of the stator during the operation of the pump, firstly, a spring or/and a pin with the tail end always contacting high-pressure working fluid are/is arranged at the bottom of each blade to form an effective pressure area of the bottom of each blade, then, a sectionally added effective pressure area of the bottom of each blade is arranged on each blade, and a sectionally switched intermittent liquid distribution channel communicated with the high-pressure working fluid is arranged between a space corresponding to the sectionally added effective pressure area and a corresponding adjacent working cavity; the pump has high working pressure, high total efficiency and reliable performance, and can be produced by using the existing equipment and process.

Description

Rotor blade assembly and hydraulic vane pump

Technical Field

The invention relates to a hydraulic pump, in particular to a rotor blade assembly capable of regulating and controlling pressing force of blades and blade grooves and correcting radial distribution of the pressing force, and relates to a hydraulic vane pump which is provided with the rotor blade assembly and has two effective pressure areas at the bottom of the blades.

Background

For a hydraulic vane pump to work properly, the pump must maintain contact between the vane tips and the inner surface of the stator throughout operation.

In order to improve the working pressure of the hydraulic vane pump, the problem that the inner surface of the stator fails due to abrasion because the contact stress between the head of the vane and the inner surface of the stator is too large is firstly solved.

"because the radial variation gradient of the double-acting slideway (stator inner surface of each action) is bigger, the blade in the oil suction zone (stator inner surface expanding section) is required to have bigger radial acceleration to ensure that the outer end part of the blade does not break away from the slideway (stator inner surface), because of the influence of the kinetic friction force and the like, the centrifugal force of the blade cannot meet the requirement, therefore, the pump usually leads the bottom of the blade (tank bottom cavity) to be always connected with the oil discharge cavity (high-pressure working fluid) of the pump through the annular groove on the port plate (end cover), and leads the blade in the oil suction zone to extend out quickly by means of the hydraulic pressure. However, for a pump with a high working pressure, the hydraulic pressure introduced into the bottom (bottom cavity) of the vane slot significantly exceeds the force required for extending the vane, so that the contact stress between the vane (head) and the slide (inner surface of the stator) in the section is too large, the friction resistance is increased, the mechanical efficiency is reduced, the wear of the contact surface is aggravated, particularly near the end point of the oil suction section, and the overhung part of the vane is broken off due to too large tangential resistance of the end (head) of the vane in serious cases. "

"(existing hydraulic primary-secondary vane pumps, hydraulic pin vane pumps, hydraulic double vane pumps and the like) is to try to reduce the effective pressure area of the bottom of the vane by a certain structure. "

The contents of the above two citations, except for the text in parentheses, are taken from the handbook of hydropneumatic technology, published by the mechanical industry press, p.484.

In order to maintain the normal operation and good performance of the hydraulic vane pump, the pump should ensure that the vanes can overcome the pressing force on the front side and the rear side of the vane slot and maintain proper contact stress on the inner surface of the stator in different sections under the action of liquid pressure and rotary centrifugal force in the whole operation process. The hydraulic vane pump which reduces the effective pressure area at the bottom of the vane is adopted to always configure high-pressure working fluid for the effective pressure area in work through the annular groove which is always connected with the high-pressure working fluid on the end cover, and the working pressure of the hydraulic vane pump is feasible within a certain range.

The existing hydraulic master-slave vane pump, hydraulic pin vane pump and double vane pump, etc. which try to reduce the effective pressure area of the vane bottom by a certain structure, corresponding to the working rotation direction of the rotor, when the vane with a contact angle contacts with the inner surface of the stator, the contact part divides the vane head into the front part of the vane head and the back part of the vane head, when the two contact angles of the vane with two contact angles contact with the inner surface of the stator simultaneously, the two contact parts divide the front part of the vane head, the middle part of the vane head and the back part of the vane head, they basically adopt the structure as shown in fig. 3.4-29 in 485 pages of the hydropneumatic technical manual, and a balanced liquid distribution channel is arranged between the groove bottom cavity where the vane is located and the working cavity communicated with the larger area of the vane head; however, the above structure makes the corresponding blade located at the maximum radial position, and when the front working chamber of the blade contains high-pressure working fluid and the rear working chamber of the blade contains low-pressure working fluid, the pressure of the front side surface of the blade contacting the high-pressure working fluid or contacting the high-pressure working fluid and the fluid film forms a larger blade groove rear side pressure force to the blade groove where the blade is located; when the corresponding blade is located at the minimum radial position, the rear side working cavity of the blade contains high-pressure working fluid, and the front side working cavity contains low-pressure working fluid, the pressure of the rear side surface of the blade contacting the high-pressure working fluid or the high-pressure working fluid and a fluid film forms larger front side pressing force of the blade groove on the blade groove where the blade is located, the pressing force of the front side and the rear side of the blade groove puts forward corresponding requirements on the design of the size of the effective pressure-bearing area, and the hydraulic force generated by the effective pressure-bearing area of the bottom of the blade with the overlarge pressure-bearing area enables the head of the blade and the diameter-expanding section of the inner surface of the stator to have high contact stress, so that the contact stress of the head of the blade and the diameter-expanding section of the inner surface of the stator cannot be well controlled under the condition of higher working pressure, accelerated wear of part of the inner surface of the stator is caused, and the working performance of the hydraulic vane pump is deteriorated.

Receive above-mentioned hydraulic vane pump rotor blade subassembly's current structural limitation, it is great to have led to above-mentioned effective pressurized area, makes the hydraulic vane pump operating pressure who adopts this rotor blade subassembly can not further improve, needs to improve to the structural defect that above-mentioned rotor blade subassembly exists.

The annular groove connected with the high-pressure working fluid is formed in the end cover of the hydraulic vane pump, so that the movement gap between the rotor blade assembly and the end cover increases the internal leakage amount of the generated working fluid, and the working volume efficiency of the pump is reduced; the volume of the space corresponding to the effective area is expanded to suck high-pressure working fluid from the annular channel of the end cover, so that the geometric displacement of the pump is reduced, the volumetric efficiency of the pump is actually further reduced, the further improvement of the working pressure of the pump is limited, and further improvement is needed for overcoming the structural defects of the hydraulic vane pump.

In order to ensure that the hydraulic vane pump is suitable for continuously developing towards the directions of high pressure, energy conservation, high efficiency and environmental protection, and low-viscosity fluid or high-water-based working medium is suitable for use, the defects of the rotor vane assembly and the defects of the hydraulic vane pump need to be further improved.

Disclosure of Invention

The first technical problem to be solved by the invention is to provide a rotor blade assembly which can adjust the contact force of control blades and rotor blade grooves and can correct the radial distribution of the contact force, aiming at the defects of the rotor blade assembly of the existing hydraulic vane pump.

The second technical problem to be solved by the present invention is to provide a hydraulic vane pump which can adjust the contact force of the control vane and the rotor vane slot, correct the radial distribution of the contact force, have various effective pressure bearing areas at the vane bottom, and improve the working pressure, aiming at the defects of the hydraulic vane pump.

The technical scheme adopted by the invention for solving the first technical problem is as follows:

a rotor blade assembly, comprising: the blade is arranged in the inner cavity of the hydraulic vane pump stator and provided with a rotor which is distributed with a plurality of blade grooves along the circumference and can rotate, and the head part of the blade is provided with a contact angle or two contact angles and can be arranged in the blade grooves in a telescopic motion way;

a groove bottom cavity can be formed between the tail end of the blade and the bottom of the blade groove under the matching of two end covers positioned at two axial ends of the stator; two adjacent blades, the radial outer surface of the rotor and the inner surface of the stator are matched with two end covers positioned at two axial ends of the stator to form a working cavity;

corresponding to the working rotation direction of the rotor: rear side matching surfaces which can be contacted mutually exist between part of the rear side surfaces of the blades and the corresponding rear side surfaces of the blade grooves, and front side matching surfaces which can be contacted mutually exist between part of the front side surfaces of the blades and the corresponding front side surfaces of the blade grooves; the contact part of the blade of one contact angle and the inner surface of the stator divides the blade head into a front part of the blade head and a back part of the blade head; the blade head is divided into a blade head front side part, a blade head middle part and a blade head rear side part at two contact positions of the blades with the two contact angles and the inner surface of the stator;

the blade adopts a contact angle: a groove bottom cavity rear side balancing channel is arranged in a corresponding part of the rotor between a rear side working cavity communicated with the rear side part of the head part of the blade and a groove bottom cavity where the blade is located, or a groove bottom cavity front side balancing channel is arranged in a corresponding part of the rotor between a front side working cavity communicated with the front side part of the head part of the blade and a groove bottom cavity where the blade is located; the blade adopts two contact angles: a middle balancing channel of the bottom cavity of the groove is arranged between the middle part of the head of the blade and the bottom cavity of the groove where the blade is positioned in the corresponding part of the blade;

the method is characterized in that:

a rear side balancing chamber is arranged on the rear side surface of the blade or/and the rear side surface of the blade groove within the range of part of the rear side matching surface corresponding to the rear side matching surface of the blade at the maximum radial position;

a front side matching surface corresponding to the front side of the vane at the minimum radial position is provided with a front side balance chamber on the front side surface of the vane or/and the front side surface of the vane slot within the range of part of the front side matching surface;

the rear side balance chamber and the front side balance chamber corresponding to the same blade are communicated all the time, during work, the working fluid pressure in the rear side balance chamber corresponding to the blade located at the maximum position is determined by the working fluid pressure in the front side balance chamber corresponding to the blade located at the minimum position, and the working fluid pressure in the front side balance chamber corresponding to the blade located at the minimum position is determined by the working fluid pressure in the rear side balance chamber corresponding to the blade located at the minimum position.

As a further improvement: a rear side liquid distribution passage for communicating the former with the latter is provided in the corresponding part of the vane or the vane and the rotor, and the rear side liquid distribution passage is terminated to communicate the former with the latter in the displacement before the vane retracts to the minimum radial position in the operation; the blade is provided with a middle balance channel with a groove bottom cavity, a rear side matching surface corresponding to the rear side balance chamber and reserved in the arrangement, a part of the rear side surface of the blade in the reserved rear side matching surface is taken as the former, a rear side working cavity of the blade is taken as the latter, and a rear side liquid distribution channel enabling the former to be communicated with the latter is arranged in the corresponding part of the blade or the blade and the rotor.

In the working process that the working cavities on the front side and the rear side of the blade are in contact with different working pressures, the improved rotor blade assembly can adjust and control the clinging force of the blade and a rotor blade groove, and can also correct the radial distribution of the pressing force, so that the blade is in a stable state to perform working displacement.

The technical solution adopted to solve the second technical problem of the present invention is:

a hydraulic vane pump, comprising: the device comprises a pump shell with a fluid inlet and a fluid outlet, a stator which is arranged in the pump shell and provided with one or more groups of diameter expanding sections and diameter reducing sections corresponding to the rotation direction of a rotor on the surface of an inner cavity, a left end cover and a right end cover which are arranged at two axial ends of the stator, a rotor with a plurality of blade grooves distributed along the circumference and blades arranged in the blade grooves and a transmission shaft which is arranged at one side of the pump shell in a penetrating way and is linked with the rotor;

two adjacent extended blades, the radial outer surface of the rotor, the inner surface of the stator, the left end cover and the right end cover correspondingly form a working cavity;

the left end cover and the right end cover: the pump casing is provided with a suction inlet and a working cavity, the suction inlet is arranged between the suction inlet and the working cavity is in contact with the diameter-expanded section of the inner surface of the stator, the discharge outlet is arranged between the discharge outlet and the working cavity is in contact with the diameter-reduced section of the inner surface of the stator, the discharge outlet is provided with an auxiliary channel, one end of the auxiliary channel is communicated with the discharge outlet, and the circumferential positions of the extension suction inlet, the extension discharge outlet and the auxiliary channel in the left end cover and the right end cover respectively correspond to each other; the extension suction inlet and the extension discharge outlet are arranged at intervals along the circumferential direction and cannot be communicated with the same working cavity at the same time; during work, the working cavity contacting with the diameter expanding section guides suction pressure working fluid into the cavity from the outside of the pump when the volume is increased, and the working cavity contacting with the diameter reducing section discharges discharge pressure working fluid out of the cavity when the volume is reduced;

the method is characterized in that: the rotor and the blades in the inner cavity of the stator of the hydraulic vane pump adopt the rotor blade assembly.

As a further improvement: the pin and/or the spring are/is additionally arranged in the rotor blade assembly; the added pin is as follows: the bottom of the blade groove of the rotor with the inner hole bushing is provided with a pin hole, and a pin is arranged in the pin hole; a pin bottom cavity is formed between the tail of the pin and the bottom of the pin hole; an annular channel communicated with each pin bottom cavity is arranged in the rotor, a plurality of inclined hole channels are arranged between the annular channel and two axial end faces of the rotor, and the annular channel and the inclined hole channels form a pin bottom cavity liquid distribution channel; the radial positions of the inclined hole channels of the liquid distribution channel of the pin bottom cavity at two axial end faces of the rotor respectively correspond to the auxiliary channels in the left end cover and the right end cover, and at least one inclined hole channel in the liquid distribution channel of the pin bottom cavity is communicated with the auxiliary channels in the left end cover and the right end cover, so that the tail part of the pin is always in contact with and discharges pressure working liquid in the whole working process; the additional spring is as follows: spring holes are arranged between the blades and the rotor and on corresponding parts, and springs are arranged in the spring holes; the axial position arrangement of the pin or/and the spring is determined by the bottom axial balanced stress requirement of the corresponding blade in the working process; the vane is in contact with the inner surface of the stator, and the radial area of the pin contacting with the pressure working fluid to be discharged or/and the working load of the spring are designed correspondingly.

According to the working pressure of the hydraulic vane pump, the working load of the spring can be converted into different blade bottom pressure areas, and the radial area of the pin or/and the working load of the spring are/is used for configuring the effective pressure area of the blade bottom. When the front working cavity and the rear working cavity of the vane work at the same time to be communicated with the extending suction inlet, the improved hydraulic vane pump at least ensures that the vane is contacted with the inner surface of the stator.

The first further improvement and further improvement in the technical solution adopted to solve the second technical problem of the present invention is:

as a further improvement: the rotor blade assembly adopts a contact angle blade, another pin is additionally arranged in the rotor blade assembly, another pin hole is arranged at the bottom of the blade groove and axially departs from the pin hole, and another pin is arranged in the other pin hole; the axial position of the other pin is determined by the bottom axial balanced stress requirement of the corresponding blade in the working process; another pin bottom cavity is formed between the tail end of the other pin and the bottom of the other pin hole, and the other pin bottom cavity where the other pin is located is the other pin bottom cavity corresponding to the other pin connecting blade; another pin bottom cavity rear side intermittent liquid distribution channel is arranged between the rear side working cavity of the blade and another pin bottom cavity corresponding to the blade in the corresponding part of the rotor blade assembly, and the other pin bottom cavity rear side intermittent liquid distribution channel is used for enabling the blade rear side working cavity to be communicated with the other pin bottom cavity corresponding to the blade when the corresponding blade is positioned at the minimum radial position and the smaller radial position; another pin bottom cavity front side intermittent liquid distribution channel is arranged in a corresponding part of the rotor blade assembly between the front side working cavity of the blade and the other pin bottom cavity corresponding to the blade, and the other pin bottom cavity front side intermittent liquid distribution channel is used for enabling the blade front side working cavity to be communicated with the other pin bottom cavity corresponding to the blade when the corresponding blade is positioned at the maximum and larger radial positions; during operation, the other pin bottom cavity corresponding to the blade is communicated with the rear side working cavity of the blade through the other pin bottom cavity rear side intermittent liquid distribution channel or/and is communicated with the front side working cavity of the blade through the other pin bottom cavity front side intermittent liquid distribution channel.

An auxiliary channel in the end cover enables a bottom cavity of the pin to be always configured with high-pressure working fluid; the other side cavity of the front side and the back side cavity of the pin bottom cavity are provided with intermittent liquid distribution channels, so that the corresponding blade and the other pin become a valve core of the two-position three-way reversing valve, a liquid distribution structure for enabling the other side cavity of the pin bottom cavity to obtain the sectional adjusting working liquid pressure in the working period is simplified, simultaneously, the corresponding other side cavity of the pin bottom cavity can lead the sucked pressure working liquid into the cavity through the corresponding working cavity in the volume expansion process, and can enable the corresponding other side cavity of the pin bottom cavity to discharge the pressure working liquid out of the cavity through the corresponding working cavity in the volume reduction process, thereby improving the working displacement of the pump, correspondingly reducing the flow pulsation of the working liquid in the pump, reducing the working noise of the pump, simultaneously accommodating the working condition of low-pressure working liquid in the front side and the back side working cavities, and avoiding the generation of hydraulic force for enabling the blade to stretch to the outer diameter by the total effective area of the other side cavity corresponding to the same blade, and further improving the mechanical efficiency of the pump; meanwhile, the annular channels arranged in the end covers are reduced, the internal leakage amount of working liquid of the two axial end faces of the rotor blade assembly is reduced during working, the volumetric efficiency of the pump is further improved, and the purpose of further improving the working pressure of the hydraulic vane pump is achieved on the premise of ensuring the normal working of the pump.

As a further refinement: the rotor blade assembly;

adopt groove bottom chamber rear side balanced passageway: the radial area of the front part of the blade head, which is communicated with the extension suction inlet, is correspondingly designed when the blade is kept in contact with the inner surface of the stator in the process of utilizing the working fluid pressure difference; the other pin radial area which is connected with the blade and is communicated with the extension outlet is correspondingly designed and additionally arranged when the blade is required to be kept in contact with the inner surface of the stator in the process of utilizing the pressure difference of the working fluid;

adopt groove bottom chamber front side balanced passageway: the radial area of the rear part of the blade head, which is communicated with the extension suction inlet, is correspondingly designed when the blade is kept in contact with the inner surface of the stator in the process of utilizing the working fluid pressure difference; the corresponding back side working cavity is communicated with the extended discharge port, the front side working cavity is communicated with the extended suction port and contacts with the blade in working of working fluid with different pressure, and in order to enable the blade to keep contact with the inner surface of the stator in the process of utilizing the pressure difference of the working fluid, another pin radial area which is connected with the blade and is communicated with the extended discharge port is correspondingly designed.

In operation, the further pintle radial area is used to provide a blade bottom effective pressure area that is additive to the blade configuration section to which the further pintle is coupled.

The effective pressure area of the bottom of the blade mainly comprises: in the work that working cavities at the front side and the rear side of each blade contain working fluid with different pressures and a corresponding groove bottom cavity contains high-pressure working fluid, the sum of the radial area of a pin corresponding to the blade, the radial area of another pin and the area of the tail part of the residual blade is used as the effective pressure bearing area of the bottom of the blade; in the work that working cavities at the front side and the rear side of each blade contain working fluid with different pressures and a corresponding groove bottom cavity contains low-pressure working fluid, the sum of the radial area of a pin corresponding to the blade and the radial area of another pin is used as the effective pressure-bearing area of the bottom of the blade; in the work that the working chambers on the front side and the rear side of the blade simultaneously contain low-pressure working fluid, the radial area of the corresponding pin of the blade is used as the effective pressure-bearing area of the She Piande part.

The difference setting of the effective pressurized area of the bottom of the blade corresponding to different working conditions enables the contact stress of the head of the blade and the inner surface of the stator in different working conditions to be properly and flexibly adjusted, the mechanical efficiency of the pump is improved, and the service life of the pump is prolonged.

The second re-improvement and further re-improvement scheme adopted in the invention to solve the second technical problem is as follows:

as a further improvement: the rotor blade assembly adopts a contact angle blade, a blade middle cavity is additionally arranged in the rotor blade assembly, a groove is formed in the lower part of the blade and axially departs from the pin, and a sub-blade is arranged in the groove; the lower part of the blade, the sub-blade and the blade groove correspondingly form a blade middle cavity corresponding to the blade; the axial position of the blade middle cavity is determined by the bottom axial balanced stress requirement of the corresponding blade in the working process; an intermittent liquid distribution channel at the rear side of the middle cavity is arranged between the working cavity at the rear side of the blade and the middle cavity of the blade corresponding to the blade in the corresponding part of the rotor blade assembly, and the intermittent liquid distribution channel at the rear side of the middle cavity is used for enabling the working cavity at the rear side of the blade on the minimum radial position and the smaller radial position of the corresponding blade to be communicated with the middle cavity of the blade corresponding to the blade; an intermediate cavity front side intermittent liquid distribution channel is arranged between the front side working cavity of the blade and the blade intermediate cavity corresponding to the blade in the corresponding part of the rotor blade assembly, and the intermediate cavity front side intermittent liquid distribution channel is used for enabling the blade front side working cavity to be communicated with the blade intermediate cavity corresponding to the blade when the corresponding blade is positioned at the maximum radial position and the larger radial position; during working, the blade middle cavity corresponding to the blade is communicated with the rear side working cavity of the blade through the middle cavity rear side intermittent liquid distribution channel or/and communicated with the front side working cavity of the blade through the middle cavity front side intermittent liquid distribution channel.

The auxiliary channel in the end cover enables the bottom cavity of the pin to be always matched with high-pressure working fluid; the arrangement of the intermittent liquid distribution channels of the bottom cavities of the front side pin and the rear side pin enables the corresponding blades to become valve cores of the two-position three-way reversing valve, simplifies a liquid distribution structure for enabling the middle cavities of the blades to obtain sectional adjusting working liquid pressure in a working period, simultaneously enables the corresponding middle cavities of the blades to guide suction pressure working liquid into the cavities through the corresponding working cavities in volume expansion, enables the corresponding middle cavities of the blades to discharge the pressure working liquid in the cavities to the outside of the pump through the corresponding working cavities in volume reduction, improves the working discharge capacity of the pump, correspondingly reduces the flow pulsation of the working liquid in the pump, reduces the working noise of the pump, does not generate hydraulic force for enabling the blades to stretch to the outer diameter in the working process that the corresponding middle cavities of the blades simultaneously accommodate low-pressure working liquid in the working cavities at the front side and the rear side pin, and further improves the mechanical efficiency of the pump; meanwhile, the annular channels arranged in the end covers are reduced, the internal leakage amount of working liquid of the two axial end faces of the rotor blade assembly is reduced during working, the volumetric efficiency of the pump is further improved, and the purpose of further improving the working pressure of the hydraulic vane pump is achieved on the premise of ensuring the normal working of the pump.

As a further refinement: the rotor blade assembly;

adopt groove bottom chamber rear side balanced passageway: the front part of the blade head, which is communicated with the extended suction inlet, is designed correspondingly to keep the blade in contact with the inner surface of the stator in the process of utilizing the pressure difference of the working fluid, so that the radial area of the front part of the blade head, which is communicated with the extended suction inlet, is designed correspondingly; the corresponding front side working cavity is communicated with the extension outlet, the rear side working cavity is communicated with the extension inlet and contacts with the blade in working of working fluid with different pressure, and the radial area of the middle cavity of the blade, which corresponds to the blade and is communicated with the extension outlet, is correspondingly designed and additionally increased when the blade keeps contact with the inner surface of the stator in the process of utilizing the pressure difference of the working fluid;

adopt groove bottom chamber front side balanced passageway: the radial area of the rear part of the head of the blade communicated with the extended suction inlet is correspondingly designed for keeping the blade in contact with the inner surface of the stator in the process of utilizing the working fluid pressure difference; the blade is contacted with the blade in working of working fluid with different pressure by the corresponding rear working cavity communicated with the extended discharge port and the front working cavity communicated with the extended suction port, and the radial area of the middle cavity of the blade, which is corresponding to the blade and communicated with the extended discharge port, is additionally designed correspondingly to ensure that the blade is kept in contact with the inner surface of the stator in the process of utilizing the pressure difference of the working fluid.

In operation, the radial area of the vane intermediate chamber is used to configure a segmental effective pressure receiving area of the vane bottom for the corresponding vane of the vane intermediate chamber.

The effective pressure area of the bottom of the blade mainly comprises: during the work that working cavities at the front side and the rear side of the blade contain working liquid with different pressures and a corresponding groove bottom cavity contains high-pressure working liquid, the sum of the radial area of a pin, the radial area of a middle cavity of the blade and the area of the tail part of the residual blade corresponding to the blade is used as the effective pressure bearing area of the bottom of the blade; working cavities at the front side and the rear side of the blade contain working liquids with different pressures, and a corresponding groove bottom cavity contains low-pressure working liquid, wherein the sum of the radial area of a pin corresponding to the blade and the radial area of a middle cavity of the blade is used as the effective pressure-bearing area of the bottom of the blade; in the work that the working chambers on the front side and the rear side of the blade simultaneously contain low-pressure working fluid, the radial area of the corresponding pin of the blade is used as the effective pressure-bearing area of the She Piande part.

The third and further improvement of the technical solution adopted by the present invention to solve the second technical problem is:

as a further improvement: the rotor blade assembly adopts two contact angle blades, a groove bottom cavity rear side intermittent liquid distribution channel is arranged between a rear side working cavity of each blade and a groove bottom cavity where the blade is located in a corresponding part of the rotor blade assembly, and the groove bottom cavity rear side intermittent liquid distribution channel is used for enabling the rear side working cavity of each blade located on the minimum radial position and the smaller radial position of the corresponding blade to be communicated with the groove bottom cavity where the blade is located; a groove bottom cavity front side intermittent liquid distribution channel is arranged between the front side working cavity of the blade and the groove bottom cavity of the rotor blade component in the corresponding part of the corresponding part, and is used for enabling the blade front side working cavity to be communicated with the groove bottom cavity of the blade at the maximum radial position and the larger radial position of the corresponding blade; when the middle part of the blade head contacts the diameter expanding section and the front contact angle of the blade head is separated from the inner surface of the stator, a front clearance channel is generated between the middle part of the blade head and the front working cavity, or when the middle part of the blade head contacts the diameter reducing section and the rear contact angle of the blade head is separated from the inner surface of the stator, a rear clearance channel is generated between the middle part of the blade head and the rear working cavity; in operation, the middle balance channel of the bottom cavity of the blade is matched with the front clearance channel or the rear clearance channel, and the bottom cavity of the blade is at least communicated with the adjacent working cavity of the blade by combining the rear intermittent liquid distribution channel of the bottom cavity of the blade and the front intermittent liquid distribution channel of the bottom cavity of the blade.

The auxiliary channel in the end cover enables the bottom cavity of the pin to be always matched with high-pressure working fluid; the arrangement of the intermittent liquid distribution channels of the bottom cavities of the front side pin and the rear side pin enables the corresponding blades to become valve cores of the two-position three-way reversing valve, simplifies a liquid distribution structure which enables the tank bottom cavities to obtain sectional adjustment working liquid pressure in a working period, simultaneously enables the corresponding tank bottom cavities to guide suction pressure working liquid into the cavities through the corresponding working cavities in volume expansion, enables the corresponding tank bottom cavities to discharge pressure working liquid in the cavities to the outside of the pump through the corresponding working cavities in volume reduction, improves the working displacement of the pump, correspondingly reduces the flow pulsation of the working liquid in the pump, reduces the working noise of the pump, does not generate hydraulic force which enables the blades to stretch to the outer diameter in the work when the working cavities on the front side and the rear side simultaneously contain low-pressure working liquid, and further improves the mechanical efficiency of the pump; meanwhile, the annular channels arranged in the end covers are reduced, the internal leakage amount of working liquid of the two axial end faces of the rotor blade assembly is reduced during working, the volumetric efficiency of the pump is further improved, and the purpose of further improving the working pressure of the hydraulic vane pump is achieved on the premise of ensuring the normal working of the pump.

As a further refinement: the rotor blade assembly;

adopts a middle balance channel of a tank bottom cavity: the radial area of the front part of the blade head, which is communicated with the extension suction inlet, is correspondingly designed when the blade is kept in contact with the inner surface of the stator in the process of utilizing the working fluid pressure difference; the radial area of the back part of the blade head communicated with the extended suction inlet is correspondingly designed to ensure that the blade is kept in contact with the inner surface of the stator in the process of utilizing the working fluid pressure difference.

The middle balance channel of the slot bottom cavity ensures that the hydraulic force of the same external diameter stretching of the blade is not generated between the blade tails with the same radial area as the middle part of the head of the blade, and the radial area of the hydraulic action of the bottom of the blade is determined by the sum of the radial area of the front part of the head of the blade and the radial area of the rear part of the head of the blade.

The effective pressure area of the bottom of the blade at least comprises:

in the work that working cavities at the front side and the rear side of the blade contain working fluid with different pressures and high-pressure working fluid at the same time, the sum of the radial area of a hydraulic action part at the bottom of the blade corresponding to the blade and the radial area of a pin is used as the effective pressure-bearing area at the bottom of the blade; in the work that the working cavities on the front side and the rear side of the blade simultaneously contain low-pressure working fluid, the radial area of the corresponding pin of the blade is used as the effective pressure bearing area of the bottom of the blade;

according to the working pressure of the hydraulic vane pump, the working load of the spring can be converted into different pressed areas of the bottom of the vane; when the working load of the spring can meet the requirement that the blade keeps in contact with the inner surface of the stator and a pin is cancelled when the working cavities at the front side and the rear side of the blade are simultaneously communicated with the extending suction inlet, in the work that the working cavities at the front side and the rear side of the blade contain working fluids with different pressures and simultaneously contain high-pressure working fluid, the sum of the radial area of the hydraulic action part at the bottom of the blade corresponding to the blade and the radial area converted by the working load of the spring is used as the effective pressure-bearing area at the bottom of the blade; and in the work that the working cavities on the front side and the rear side of the blade simultaneously contain low-pressure working fluid or high-pressure working fluid, the radial area converted by the working load of the corresponding spring of the blade is used as the effective pressure bearing area of the bottom of the blade.

In conclusion, the improved hydraulic vane pump has the characteristics of high working pressure, small flow pulsation, low noise, large power-mass ratio, small leakage coefficient, high volumetric efficiency, high mechanical efficiency, long service life, strong self-priming capability and large rated rotating speed amplitude; the pump is more suitable for adopting low-viscosity fluid or high-water-based working medium, better accords with the development requirement of the hydraulic vane pump to the high-pressure, energy-saving, high-efficiency and environment-friendly direction, and can realize the adjustment of the working flow in unit time by controlling the working speed of the pump in the working process corresponding to the characteristic of large rated speed amplitude of the pump.

The invention also has the following beneficial effects: because the hydraulic vane pump has the characteristic of high working pressure, the pump can replace a hydraulic plunger pump in a wider range for use, when the hydraulic vane pump is used in a high-pressure hydraulic system, the purchase cost of the high-pressure hydraulic system is reduced, and the working noise of the high-pressure hydraulic system is controlled; the hydraulic vane pump has the characteristics of small leakage coefficient and high volumetric efficiency, and further expands the use occasions of the hydraulic vane pump, so that the development of the high water-based transmission element and the water transmission element technology is promoted, the use cost of the hydraulic system is reduced, and the hydraulic system is more in line with the environmental protection requirement.

Drawings

Fig. 1 is a sectional view of a double-acting hydraulic vane pump in embodiment 1;

FIG. 2 is an exploded view of the rotor blade assembly of FIG. 1;

FIG. 3 is a schematic structural view of the left end cap in embodiment 1;

FIG. 4 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 3;

FIG. 5 is a schematic view of a structure of a stator in embodiment 1;

FIG. 6 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 5;

FIG. 7 is a schematic view of the structure of a rotor in embodiment 1;

FIG. 8 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 7;

FIG. 9 is a schematic end view of the structure of FIG. 7;

FIG. 10 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 9;

FIG. 11 is a schematic structural view of a right end cap in embodiment 1;

FIG. 12 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 11;

FIG. 13 is a perspective view schematically showing the structure of the blade in embodiment 1;

FIG. 14 is a structural view schematically showing another perspective of the blade in embodiment 1;

FIG. 15 is a structural view schematically showing still another perspective of the blade in embodiment 1;

FIG. 16 isbase:Sub>A sectional view taken along line A-A of FIG. 14;

FIG. 17 is a schematic view of the structure of FIG. 14 in direction A;

FIG. 18 is a sectional view taken along line B-B of FIG. 14;

FIG. 19 is a three-dimensional view of the blade in embodiment 1;

FIG. 20 is a three-dimensional view from another perspective of the blade in embodiment 1;

FIG. 21 is a schematic structural view of another pin in example 1;

FIG. 22 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 21;

FIG. 23 is a schematic view of the alternate view structure of FIG. 21;

FIG. 24 is a schematic view showing a liquid distribution route of a rear side liquid distribution channel at an end face of a module in example 1;

FIG. 25 is a schematic view showing the main liquid distribution paths of the tank bottom chambers and the pin bottom chamber at one circumferential position in embodiment 1;

FIG. 26 is a schematic view showing the main liquid distribution route of each well bottom chamber and another pin bottom chamber at another circumferential position in example 1;

fig. 27 is an enlarged view of portion I of fig. 25;

FIG. 28 is a schematic structural view of a right end cap in embodiment 2;

FIG. 29 isbase:Sub>A sectional view taken along line A-A of FIG. 28;

FIG. 30 is a schematic structural view of a left end cap in embodiment 2;

FIG. 31 isbase:Sub>A sectional view taken along line A-A of FIG. 30;

FIG. 32 is a schematic view of a structure of a stator in embodiment 2;

FIG. 33 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 32;

FIG. 34 is a schematic view of a structure of a rotor in embodiment 2;

FIG. 35 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 34;

FIG. 36 is a schematic view showing the main liquid distribution paths of the tank bottom chambers and the pin bottom chamber at one circumferential position in embodiment 2;

FIG. 37 is a schematic structural view of a rotor in embodiment 3;

FIG. 38 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 37;

FIG. 39 is a structural view schematically showing a blade in accordance with embodiment 3;

FIG. 40 is a structural view schematically showing another perspective of the blade in embodiment 3;

FIG. 41 is a schematic view showing a structure of a blade in accordance with embodiment 3 from a further perspective;

FIG. 42 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 40;

FIG. 43 is a schematic view of the A-direction structure of FIG. 40;

FIG. 44 is a cross-sectional view taken along line B-B of FIG. 40;

FIG. 45 is a three-dimensional view of a blade in embodiment 3;

FIG. 46 is a three-dimensional view from another perspective of the blade of embodiment 3;

FIG. 47 is a schematic structural view of another pin according to embodiment 3;

FIG. 48 isbase:Sub>A sectional view taken along line A-A of FIG. 47;

FIG. 49 is a schematic view showing a liquid distribution route of a rear liquid distribution channel at an end face of a module in example 3;

FIG. 50 is a schematic view showing the main liquid distribution paths of the tank bottom chambers and another pin bottom chamber at one circumferential position in example 3;

FIG. 51 is a schematic view showing the main liquid distribution route of each well bottom chamber and another pin bottom chamber at another circumferential position in example 3;

FIG. 52 is a schematic view showing the main liquid distribution route of each well bottom chamber and another pin bottom chamber at still another circumferential position in example 3;

FIG. 53 is an enlarged view of portion I of FIG. 51;

FIG. 54 is an enlarged view of section II of FIG. 51;

FIG. 55 is a schematic view showing the structure of a rotor in embodiment 4;

FIG. 56 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 55;

FIG. 57 is a structural view schematically showing a blade in embodiment 4 from a viewpoint;

FIG. 58 is a structural view schematically showing another perspective of the blade in embodiment 4;

FIG. 59 is a schematic view showing a structure of a blade in accordance with embodiment 4;

FIG. 60 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 58;

FIG. 61 is a schematic view of the structure of FIG. 58 in direction A;

FIG. 62 is a cross-sectional view taken along line B-B of FIG. 58;

FIG. 63 is a three-dimensional view of the blade in embodiment 4;

FIG. 64 is a three-dimensional view from another perspective of the blade of embodiment 4;

FIG. 65 is a schematic structural view of a neutron blade in example 4;

FIG. 66 isbase:Sub>A sectional view taken along line A-A of FIG. 65;

FIG. 67 is a schematic view showing a liquid distribution route of a rear side liquid distribution channel at an end face of a module in example 4;

FIG. 68 is a schematic view of the main liquid distribution route of each of the tank bottom chambers and the vane intermediate chambers in one circumferential position in example 4;

FIG. 69 is a schematic view showing the main liquid distribution route of each of the tank bottom chambers and the vane intermediate chambers in another circumferential position in example 4;

FIG. 70 is an enlarged view of portion I of FIG. 68;

FIG. 71 is a schematic structural view of a rotor in embodiment 5;

FIG. 72 isbase:Sub>A sectional view taken along line A-A of FIG. 71;

FIG. 73 is a schematic view of the main liquid distribution route of each of the tank bottom chambers and the vane intermediate chambers in one circumferential position in example 5;

FIG. 74 is a structural view schematically showing a blade in accordance with embodiment 6;

FIG. 75 is a schematic view showing a structure of a vane in accordance with embodiment 6;

FIG. 76 is a structural view schematically showing a further perspective of the blade in embodiment 6;

FIG. 77 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 75;

FIG. 78 is a schematic view of the A-direction structure of FIG. 75;

FIG. 79 is a sectional view taken along line B-B of FIG. 75;

FIG. 80 is a three-dimensional view of the blade in embodiment 6;

FIG. 81 is a three-dimensional view from another perspective of the blade in embodiment 6;

FIG. 82 is a schematic view of a structure of a rotor in embodiment 6;

FIG. 83 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 82;

FIG. 84 is a schematic view of the main dispensing path of the bottom chambers of the cells in one circumferential position in example 6;

FIG. 85 is a schematic view of the main liquid distribution route of each tank bottom chamber in another circumferential position in example 6;

FIG. 86 is an enlarged view of portion I of FIG. 84;

FIG. 87 is a schematic view of a rotor structure in embodiment 11;

FIG. 88 isbase:Sub>A sectional view taken along line A-A of FIG. 87;

FIG. 89 is a schematic view of the main dispensing path of the well bottom chambers in one circumferential position of example 11;

FIG. 90 is a schematic view of a rotor structure in embodiment 12;

FIG. 91 isbase:Sub>A sectional view taken along line A-A of FIG. 90;

FIG. 92 is a structural view schematically illustrating a perspective of the blade in embodiment 12;

FIG. 93 is a schematic view showing another perspective structure of the blade in embodiment 12;

FIG. 94 is a structural schematic view of a blade in accordance with embodiment 12 from a further perspective;

FIG. 95 isbase:Sub>A cross-sectional view taken along line A-A of FIG. 93;

FIG. 96 is a schematic view of the A-direction structure of FIG. 93;

FIG. 97 is a cross-sectional view taken along line B-B of FIG. 93;

FIG. 98 is a three-dimensional view of the blade of embodiment 12;

FIG. 99 is another perspective, three-dimensional view of the bucket of embodiment 12;

FIG. 100 is a schematic view showing a liquid distribution route of a rear side liquid distribution channel at an end face of a module in example 12;

FIG. 101 is a schematic view showing the main liquid distribution route of each tank bottom chamber and vane intermediate chamber in one circumferential position in example 12;

FIG. 102 is a schematic view of the main liquid distribution paths of the respective tank bottom chambers and vane intermediate chambers in another circumferential position in example 12;

fig. 103 is an enlarged view of portion I in fig. 101.

Detailed Description

The invention is described in further detail below with reference to the accompanying examples.

The rotor blade assembly in this application is housed in the hydraulic vane pump in this application.

The embodiments of the present invention are mainly explained for the general structure of the hydraulic vane pump, 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: referring to fig. 1 to 27, the present embodiment is a double-acting hydraulic vane pump, which mainly includes, referring to fig. 1 and 2: the left pump casing 1, the stator 2, the rotor 3, the blades 4, the left end cover 5, the right end cover 5-1, the pin 71, the other pin 72, the right pump casing 1-1 and the transmission shaft 10.

The pump casing in this embodiment is constituted by: the left pump shell 1 with a fluid outlet 02 and the right pump shell 1-1 with a fluid inlet 01 are formed, and a cylindrical inner cavity is arranged in the pump shell.

The inner surface of the stator 2 is provided with an expanding section and a reducing section, the rotor 3 is provided with a plurality of blade grooves which can be rotatably arranged in the inner cavity of the stator, the bottom of each blade groove is axially provided with a pin hole 711, a pin 71 is arranged in each pin hole, two axial sides of each pin hole are respectively provided with another pin hole 721, another pin 72 is arranged in each pin hole, the blades 4 can be radially and telescopically arranged in the blade grooves of the rotor, the left end cover 5 and the right end cover 5-1 are adjusted and positioned at two axial ends of the stator (see figures 3, 5 and 11) through respective positioning holes 51 and 52 and a positioning hole 21 in the stator, and the parts are arranged in the inner cavity of a pump shell after being matched and assembled; a driving shaft 10 connected with a power source corresponding to the working rotation direction of the pump is arranged in the hydraulic vane pump in a penetrating way, and a rotor 3 in the pump is linked with the shaft;

a groove bottom cavity 89 is correspondingly formed among the tail part of each blade, the bottom of the blade groove and two end covers, a working cavity 234 is correspondingly formed among each pair of two adjacent blades, rotors, stators and two end covers which extend out in the radial direction, a pin bottom cavity 712 is formed between the tail part of each pin and the bottom of the pin hole, and another pin bottom cavity 722 is formed between the tail part of each other pin and the bottom of the other pin hole (see fig. 25 and 27);

the working direction of the hydraulic vane pump can be divided into clockwise rotation or anticlockwise rotation according to the right view of fig. 1, and the working direction of the hydraulic vane pump of the embodiment adopts the clockwise rotation, so that the working rotation direction of the rotor is determined.

Corresponding to the working rotation direction of the rotor: the two working cavities adjacent to the blade are divided into a front working cavity and a rear working cavity of the blade, the contact line of the blade and the inner surface of the stator divides the head of the blade into a blade head front side part and a blade head rear side part, a rear side matching surface is formed between the rear side surface of the blade part and the corresponding rear side surface of the blade groove, and a front side matching surface is formed between the front side surface of the blade part and the corresponding front side surface of the blade groove;

the structure of the main parts adopted by the pump is described in detail with reference to the attached drawings of the specification as follows:

fig. 5 and 6 show the stator 2 adopted in the present embodiment, and the inner surface of the stator is provided with: the two-section diameter-reducing curved surface comprises two diameter-expanding section curved surfaces with continuously increasing distance away from the axis, two diameter-reducing section curved surfaces with continuously decreasing distance away from the axis, two curved surfaces with radius R connecting the diameter-expanding section curved surfaces and the diameter-reducing section curved surfaces, and two curved surfaces with radius R connecting the diameter-reducing section curved surfaces and the diameter-expanding section curved surfaces.

Fig. 3 and 4 show a left end cap 5 adopted in the present embodiment, in which: the stator comprises two extending suction ports 93 which cover the diameter expanding section of the inner surface of the stator and have an included angle of alpha 1, two extending discharge ports 94 which cover the diameter reducing section of the inner surface of the stator and have an included angle of alpha 2, two auxiliary channels 79 which are communicated with the extending discharge ports and have an included angle of alpha 3, one end of each extending suction port is communicated with a fluid suction port in a pump shell, the other end of each extending suction port is communicated with a working cavity which is in contact with the diameter expanding section of the inner surface of the stator, one end of each extending discharge port is communicated with the fluid discharge port in the pump shell, the other end of each extending discharge port is communicated with the working cavity which is in contact with the diameter reducing section of the inner surface of the stator, and the extending discharge ports and the extending suction ports are circumferentially separated and cannot be communicated with the same working cavity at the same time.

Fig. 11 and 12 show a right end cap 5-1 adopted in the present embodiment, in which: two extending suction ports 93 with an included angle alpha 1, two extending discharge ports 94 with an included angle alpha 2 and two auxiliary channels 79 which are communicated with the extending discharge ports and have an included angle alpha 3, and the liquid distribution paths, the circumferential positions, the radial positions and the shapes of the auxiliary channels are consistent with those of the left end cover. (the angles of the included angles of the extended suction inlet alpha 1, the extended discharge outlet alpha 2 and the auxiliary channel alpha 3 can be properly adjusted according to the experience of professional engineers)

Fig. 2, 7, 8, 9, and 10 show a rotor 3 adopted in this embodiment, the rotor includes an inner bore bushing 3-1, a chamfer of 1 × 45 ° is provided between the radial outer surface of the rotor and both end faces of the rotor, 10 vane grooves 39 are provided in the rotor, a pin hole 711 is provided in the center of each vane groove bottom in the axial direction, a pin 71 is provided in the pin hole, two another pin holes 721 having the same radial area are symmetrically provided on both sides in the axial direction of the pin hole, another pin 72 is provided in the another pin hole, a groove bottom chamber front side balance channel one 31 is provided between a front side working chamber of the vane and a groove bottom chamber where the vane is located, so that the corresponding groove bottom chamber becomes the extension end of the front side working chamber, an annular channel 7121 communicating each pin bottom chamber is provided in the rotor, three axial inclined bore channels 7122 capable of obtaining high pressure working fluid are provided between the annular channel and both end faces in the axial direction of the rotor, the annular channel and the axial inclined bore channels constitute a pin bottom chamber liquid distribution channel 712, the axial inclined bore channels and the axial inclined bore channels correspond to at least one of the left and right end cover channels 79 in the axial auxiliary working chamber, and at least one of the left end cover channels and the auxiliary working chamber are provided in the axial inclined bore channels, and the axial inclined channels, and the auxiliary bottom chamber.

Fig. 21, 22 and 23 show another pin 72 used in this embodiment, and a spring hole 7291 is provided in the center of the tail end of the other pin, the spring hole does not penetrate the head of the other pin, and the working load of the spring is only used for connecting the other pin with the corresponding blade.

In the action period, each working chamber which is in contact with the extension suction port 93 and the diameter expansion section of the inner surface of the stator leads suction pressure working fluid into the chamber from the outside of the pump when the volume is increased, each working chamber which is in contact with the extension discharge port 94 and the diameter reduction section of the inner surface of the stator discharges discharge pressure working fluid to the outside of the chamber when the volume is reduced, and the working fluid pressure in each working chamber has the characteristic of sectional change; the front side balance channel 31 of each tank bottom cavity enables the working hydraulic pressure in the front side working cavity corresponding to each tank bottom cavity to determine the working hydraulic pressure in the corresponding tank bottom cavity;

a difference value H generated by reducing the radius R of the arc curved surface by the radius R of the large arc curved surface of the stator is firstly taken, and then the difference value H is used as a comparison parameter in the following setting.

Another two pin holes and another two pin holes are connected with the vane as shown in FIG. 1 to form another two pin bottom cavities correspondingly; fig. 25, 26 show the main distribution paths of the slot bottom cavity and another pin bottom cavity, fig. 27 is an enlarged view of part I of fig. 25, the vane shown in fig. 27 and another pin to which the vane is coupled are located at the maximum radial position, the vane is shown as a front vane of the rear working cavity, and another pin bottom cavity and a rear working cavity are respectively provided with another pin bottom cavity rear intermittent distribution channel 0171 in the corresponding positions of the another pin and the rotor; the blade in the figure is taken as a rear blade of a front working cavity, and a front intermittent liquid distribution channel 0172 of the bottom cavity of the other pin is respectively arranged between the bottom cavity of the other pin and a groove bottom cavity which is the extension end of the front working cavity in the corresponding part of the other pin.

According to the illustrations of fig. 7, 8, 22, 23, 25, 26 and 27, the intermittent liquid distribution channel I0171 on the back side of the bottom cavity of the other pin is arranged:

the rotor is provided with a rotor part channel 01711 of the first intermittent liquid distribution channel at the rear side of the bottom cavity of the other stud, the outer diameter surface of the other stud hole is respectively provided with two annular channels in the rotor part channel in the corresponding part of the rotor, the radial edges of the annular channels of the rotor part are respectively and radially displaced by about 4/15H from the boundary line 001 where the bottom cavity of the slot is intersected with the outer diameter of the other stud hole along the initial boundary, the radial lower edge of the annular channel is separated by about 1H from the upper edge, then two radial inclined holes are arranged in the rotor, one end of each of the two radial inclined holes is communicated with the rear working cavity, the other end of each radial inclined hole is respectively communicated with the annular channel of the rotor part, and the two parts of the channels respectively form two groups of the rotor part channels 01711 of the first intermittent liquid distribution channel at the rear side of the bottom cavity of the other stud hole

Two other pin part channels of one other pin bottom cavity rear side intermittent liquid distribution channel communicated with the other pin spring hole 7291 from the outer surface of the other pin are respectively arranged in each other pin, the radial lower edge of the other pin part channel 01712 is equal to the intersection boundary line 001 of the groove bottom cavity and the other pin hole, and the radial edge of the other pin part channel is separated from the lower edge by about 11/15H;

the rotor part channel 01711 and the other pin part channel 01712 respectively form two groups of other pin bottom cavity rear side intermittent liquid distribution channels 0171 correspondingly, each channel included in the other pin bottom cavity rear side intermittent liquid distribution channel 0171 is corresponding in axial position and can be mutually matched and communicated, and the communication and disconnection between the rear side working cavity and the corresponding other pin bottom cavity are regulated and controlled by utilizing the radial telescopic displacement in the other pin working process connected with the corresponding blade.

According to the arrangement shown in FIGS. 25, 26 and 27, for the other pin bottom cavity front intermittent liquid distribution channel I0172:

in this embodiment, two other pin part channels 01712 in the other pin bottom cavity rear side intermittent liquid distribution channel I are respectively used as two other pin bottom cavity front side intermittent liquid distribution channels first 0172,

the other pin bottom cavity front side intermittent liquid distribution channel I0172 regulates and controls the connection and disconnection between a groove bottom cavity serving as the extension end of the front side working cavity and the corresponding other pin bottom cavity by utilizing the radial expansion displacement in the other pin work connected with the corresponding blade; the liquid distribution structure of the other pin bottom cavity reduces the internal leakage of the working liquid of the two axial end faces of the rotor blade assembly in the working process, and provides a favorable condition for improving the working pressure of the pump. (the sectional area and the radial position of the first intermittent liquid distribution channel at the front side of the bottom cavity of the other pin and the first intermittent liquid distribution channel at the rear side of the bottom cavity of the other pin can be properly adjusted according to the experience of professional engineers)

Referring to fig. 25 and 26, in the present embodiment, in the case where the vane is located at the maximum radial position and the front working chamber of the vane contains the high-pressure working fluid and the rear working chamber of the vane contains the low-pressure working fluid, the pressure at which the front side surface of the vane contacts the high-pressure working fluid corresponds to the rear pressing force of the vane groove, and in the case where the vane is located at the minimum radial position and the rear working chamber of the vane contains the high-pressure working fluid and the front working chamber contains the low-pressure working fluid, the pressure at which the rear side surface of the vane contacts the high-pressure working fluid and the fluid flow film corresponds to the front pressing force of the vane groove.

In the case of the working conditions described for the rear side compression force of the vane slot, as shown in fig. 13, 14, 15, 16, 18, 19, 20, 25, 26, 27, a rear balancing chamber 041 is provided on the rear side of the vane in the mating face, whose radial end boundary is smaller than the maximum radial boundary of the mating face by about 4/15H, whose axial end boundaries are smaller than the axial end boundaries of the mating face by about 1/3H, whose radial lower end boundaries are larger than the minimum radial boundary of the mating face by about 2/3H at both axial end portions and extend by about 3 and 1/5H, respectively, and whose intermediate remaining portion opens the trailing end of the vane. And correspondingly forming the working condition of the front side compression force of the blade groove, a front side balance chamber I042 is arranged on the front side surface of the blade in the corresponding matching surface, the upper end boundary of the front side balance chamber I is smaller than the maximum radial boundary of the corresponding matching surface by about 4/15H, the boundaries of the two axial ends of the front side balance chamber I are respectively smaller than the boundaries of the two axial ends of the corresponding matching surface by about 1/5H, and the lower end of the front side balance chamber I opens the tail end of the blade.

The rear side balancing chamber 041 and the front side balancing chamber 042 can be communicated with the front side working chamber through the corresponding front side balancing channels of the tank bottom cavity and the tank bottom cavity in any working condition, and the rear side balancing chamber is combined with the front side balancing chamber and used for adjusting the rear side pressing force and the front side pressing force of the blade groove.

Corresponding to a rear side matching surface reserved in the rear side balancing chamber 041, a blade part rear side liquid distribution channel 0401-1 is respectively arranged between the two lower end part blade rear side surfaces axially separated in the blade rear side surface in the reserved rear side matching surface and a rear side working cavity of the blade in the blade, the maximum radial boundary of the blade part rear side liquid distribution channel in the arrangement is level with the intersection boundary of the blade groove rear side surface and the rotor radial outer surface, a rotor part rear side liquid distribution channel 0401-2 is respectively arranged between the two part blade rear side surfaces axially separated in the blade groove rear side surface in the reserved rear side matching surface and the rear side working cavity of the blade in the rotor, the minimum radial boundary of the rotor part rear side liquid distribution channel I is about 2/3H away from the intersection boundary of the blade groove rear side surface and the rotor radial outer surface, the axial positions of a first blade part rear side liquid distribution channel 0401-1 and a rotor part rear side liquid distribution channel 0401-2 are corresponding and can be intermittently communicated with each other, the first blade part rear side liquid distribution channel 0401 and the second blade part rear side liquid distribution channel 0401-2 form a rear side liquid distribution channel 0401, the rear side liquid distribution channel I enables the rear side plane of the blade positioned on the maximum radial position to be contacted with low-pressure working liquid through chamfers of the radial outer surface of the rotor at the two axial ends, the working condition of the rear side pressure of the regulated and controlled blade groove is correspondingly formed, the radial distribution of the regulated and controlled rear side pressure of the blade groove is reasonably corrected, and therefore, the attaching trend is established between the rear side surface of the blade in the rest part of the rear side balance chamber I in the corresponding matching surface and the rear side surface of the blade groove; (see fig. 48, detail 15, 17, 18, 19, 20, 24, 25, 26, 27) taking the boundary 003 between the trailing face of the vane slot and the radially outer surface of the rotor as the support line (detail 27) for the trailing force of the trailing face of the vane slot, in this embodiment the moment of the force applied to the radially inner end of the support line is greater than the moment of the outer end of the support line, dividing the remaining portion of the trailing balance chamber in the corresponding mating face into a trailing low pressure abutment face, thereby allowing the vane in this condition to undergo an operational displacement during the corresponding abutment, and isolating the trailing balance chamber at its largest radially outer and axially opposite ends of the mating face from the trailing working chamber (detail 242 nodes of fig. 25), the trailing distribution passage not allowing a portion of the trailing face of the vane in displacement to communicate with the trailing working chamber (detail 244 nodes of fig. 26) until the vane retracts to its smallest radial position.

Corresponding to the working condition forming the front side pressing force of the regulated and controlled rear blade groove, the residual plane of the front side of the blade, positioned in the corresponding matching surface, of the front side balancing chamber 042 is directly contacted with low-pressure working fluid, so that the radial distribution of the front side pressing force of the regulated and controlled blade groove is reasonably corrected, (see details 13, 14, 19, 20, 26 and 27), a boundary line 005 of the front side surface of the blade groove and the head part of the blade is taken as a supporting line (see detail 26) of the front side pressing force of the blade groove, in the embodiment, the moment of the radial inner end of the supporting line of the pressing force is larger than the moment of the outer end of the supporting line, and the residual part of the front side balancing chamber 042 in the corresponding matching surface is used as a front side low-pressure bonding surface, so that the blade in the working condition is subjected to working displacement in automatic corresponding bonding. (see node 244 in FIG. 26 for details) (the opening depth of the balance chamber is about 2/15H; the opening depth of the balance chamber, the area of the balance chamber and the abutting surface can be adjusted according to the experience of professional engineers)

The radial area of the blade minus the radial area of the pin and the other pin that are coupled to the blade is the remaining area of the blade tail.

As shown by point 242 in fig. 25, in the operation of the vane corresponding to the rear pressing force of the vane groove, the discharge port, the first alternate pin bottom cavity front intermittent liquid distribution passage 0172, the first slot bottom cavity front balance passage 31, the auxiliary passage and the pin bottom cavity liquid distribution passage are extended, the front portion of the vane head, the tail portion of the alternate pin, the remaining vane tail portion and the pin tail portion corresponding to the same vane are respectively contacted with the high-pressure working liquid, and the suction port is extended to contact the rear portion of the vane head with the low-pressure working liquid, and the radial area of the rear portion of the vane head contacting with the low-pressure working liquid required for the vane to overcome the tendency of the rear pressing force of the vane groove to expand outward is designed; as shown by 244 in fig. 26, in the operation of the vane corresponding to the front pressing force of the vane groove, the extending discharge port, the other pin bottom cavity rear intermittent fluid distribution channel one 0172, the auxiliary channel and the pin bottom cavity fluid distribution channel respectively contact the rear part of the vane head, the other pin tail and the pin tail corresponding to the vane with high-pressure working fluid, the extending suction port, the groove bottom cavity front balancing channel one 31 respectively contact the front part of the vane head and the remaining vane tail corresponding to the vane with low-pressure working fluid, and the total radial area of the other pin and the pin corresponding to the vane is designed, wherein part of the hydraulic force generated by the total radial area is used for balancing the hydraulic force generated by the rear part of the vane head, and the remaining part of the hydraulic force is used for overcoming the front pressing force of the vane groove to keep the vane in an outward radial expansion tendency. (the radial area of the back portion of the blade head, the radial area of the pin and the radial area of the other pin can be adjusted according to the experience of the expert engineer under the requirement of ensuring that the blade maintains a proper contact stress with the inner surface of the stator during the whole operation)

Referring to fig. 25 and 26, the corresponding groove bottom cavity 89, pin bottom cavity and another pin bottom cavity are shown when the blade head contacts different circumferential nodes with the inner surface of the stator, and correspondingly, the pin tail, another pin tail and the remaining blade tail obtain the hydraulic force for extending the blade radially outward and the comparison of the total hydraulic force for retracting the blade radially inward for each part of the blade head:

in operation, as shown in point 241 in fig. 25, the front and rear working chambers of the blade are simultaneously communicated with the extension suction inlet, the corresponding bottom chamber of the blade is communicated with the front working chamber through the front balancing channel one 31 of the bottom chamber of the blade, the other bottom chamber of the pin is communicated with the front working chamber through the front intermittent liquid distribution channel one 0172 of the bottom chamber of the other pin and communicated with the rear working chamber through the rear intermittent liquid distribution channel one 0171 of the bottom chamber of the other pin, and the bottom chamber of the pin is communicated with the extension discharge outlet through the auxiliary channel and the liquid distribution channel of the bottom chamber of the pin; the front part of the blade head, the rear part of the blade head, the tail of the residual blade and the tail of another pin which correspond to the blade are all contacted with low-pressure working fluid P1, the tail of the pin is contacted with high-pressure working fluid P2, and the pin pushes the blade to keep the outward diameter expansion trend by proper hydraulic force generated by the contact of the tail of the pin and the high-pressure working fluid;

at point 242 in fig. 25, the blade front working chamber communicates with the extended exhaust port, the rear working chamber remains in communication with the extended suction port, the corresponding slot bottom chamber communicates with the front working chamber through the slot bottom chamber front balancing channel one 31, the pin bottom chamber communicates with the extended exhaust port through the auxiliary channel and the pin bottom chamber liquid distribution channel, and the other pin bottom chamber communicates with the front working chamber through the other pin bottom chamber front intermittent liquid distribution channel one 0172; the front part of the blade head, the tail part of the residual blade, the tail part of the pin and the tail part of the other pin, which correspond to the blade, are all contacted with high-pressure working fluid P2, the rear part of the blade head is contacted with low-pressure working fluid P1, and the blade is kept in the stretching trend towards the outer diameter by proper hydraulic force generated by the contact of the tail part of the pin, the tail part of the other pin and the tail part of the residual blade with the high-pressure working fluid;

at point 243 in fig. 26, the front and rear working cavities of the vane are simultaneously communicated with the extended discharge port, the corresponding bottom cavity of the vane is communicated with the front working cavity through the first balancing channel 31 at the front side of the bottom cavity of the vane, the other bottom cavity of the pin is communicated with the front working cavity through the first intermittent liquid distribution channel 0172 at the front side of the other bottom cavity of the pin and communicated with the rear working cavity through the first intermittent liquid distribution channel 0171 at the rear side of the other bottom cavity of the pin, and the bottom cavity of the pin is communicated with the extended discharge port through the auxiliary channel and the liquid distribution channel of the bottom cavity of the pin; the front part of the blade head, the rear part of the blade head, the tail of the residual blade, the tail of the pin and the tail of the other pin which correspond to the blade are all contacted with high-pressure working fluid P2, and the radial position of the blade is limited by a reducing section of the inner surface of the stator;

at 244 in fig. 26, the working cavities at the back side of the blade are communicated with the extended discharge port, the working cavities at the front side are communicated with the extended suction port, the corresponding cavity bottom cavities are communicated with the working cavities at the front side through a cavity bottom cavity front side balance channel I31, the other cavity bottom cavity of the pin is communicated with the working cavity at the back side through another cavity bottom cavity back side intermittent liquid distribution channel I0171, and the cavity bottom of the pin is communicated with the extended discharge port through an auxiliary channel and the cavity bottom cavity liquid distribution channel of the pin; the front part of the head of the blade and the tail of the residual blade corresponding to the blade are contacted with low-pressure working fluid P1, the tail of another pin, the tail of the pin and the rear part of the head of the blade corresponding to the blade are contacted with high-pressure working fluid P2, the sum of the radial area of the pin and the radial area of the other pin is larger than that of the rear part of the head of the blade, and the blade keeps the outward radial stretching trend by proper hydraulic force generated by the contact of the tail of the pin and the tail of the other pin with the high-pressure working fluid;

when the blade works to the point 241, the next working cycle is started.

The radial areas of the front part of the blade head, the rear part of the blade head, the pin and the other pin are the minimum radial areas which are respectively and correspondingly cut perpendicular to the radial axis of the corresponding blade groove;

in the whole action period, the first intermittent liquid distribution channel on the front side of the other pin bottom cavity is combined with the first intermittent liquid distribution channel on the rear side of the other pin bottom cavity, so that the suction pressure working liquid can be led into the cavity through the corresponding working cavity in the volume expansion of the corresponding other pin bottom cavity, the discharge pressure working liquid in the cavity can be discharged out of the pump through the corresponding working cavity in the volume reduction of the corresponding other pin bottom cavity, and the flow of the working liquid generated in the volume change process of the other pin bottom cavity in the work can be totally summarized into the calculated discharge capacity of the pump, thereby improving the volume efficiency of the hydraulic vane pump in the embodiment and improving the working pressure of the pump; the working fluid pressure in the corresponding other pin bottom cavity is determined by the circumferential position of the rear side working cavity and/or the front side working cavity communicated with the same on the inner surface of the stator, so that the optimal fluid distribution of the sectional adjusting pressure obtained by the corresponding other pin bottom cavity is realized, and the mechanical efficiency of the pump is improved.

In the whole action period, working cavities at the front side and the rear side of each blade contain working liquid with different pressures, and corresponding groove bottom cavities contain high-pressure working liquid, wherein the sum of the radial area of a pin corresponding to the same blade, the radial area of another pin and the area of the tail of the rest blade is used as the effective pressure-bearing area of the bottom of the blade; in the work that working cavities at the front side and the rear side of each blade contain working liquid with different pressures and a corresponding groove bottom cavity contains low-pressure working liquid, the sum of the radial area of a pin corresponding to the same blade and the radial area of another pin is used as the effective pressure-bearing area of the bottom of the blade; during the work that the working cavities on the front side and the rear side of the blade simultaneously contain low-pressure working fluid, the radial area of the pin is used as the effective pressure-bearing area of the bottom of the blade; therefore, the contact stress formed by the hydraulic force between the blade head and the inner surface of the stator of different sections is properly adjusted, and the working pressure of the pump is further improved.

Embodiment 2, referring to fig. 1, 2, 9, 10, 13 to 24, and fig. 28 to 36, this embodiment is a single-acting hydraulic vane pump, which mainly includes: the left pump casing 1, the stator 2, the rotor 3, the blades 4, the left end cover 5, the right end cover 5-1, the pin 71, the other pin 72, the right pump casing 1-1 and the transmission shaft 10.

fig. 32 and 33 show the stator 2 used in the present embodiment, in which the inner surface of the stator is provided with: 1. the section of the curved surface of the diameter-expanding section with continuously increasing distance away from the axle center, the section of the curved surface of the diameter-reducing section with continuously decreasing distance away from the axle center, the section of the curved surface of the diameter-expanding section with R as radius connecting the curved surface of the diameter-expanding section and the curved surface of the diameter-reducing section, and the section of the curved surface of the diameter-reducing section with R as radius connecting the curved surface of the diameter-reducing section and the curved surface of the diameter-expanding section.

Fig. 30 and 31 show the left end cap 5 used in the present embodiment, in which: the stator comprises an extension suction inlet I95, an extension discharge outlet I96, an auxiliary channel I80 and an auxiliary channel I, wherein the extension suction inlet I covers an expanding section of the inner surface of the stator and has an included angle of alpha 4, the extension discharge outlet I96 covers a reducing section of the inner surface of the stator and has an included angle of alpha 5, the auxiliary channel I80 is communicated with the extension discharge outlet and has an included angle of alpha 6, one end of the extension suction inlet is communicated with a fluid suction inlet in a pump shell, the other end of the extension suction inlet is communicated with a working cavity in contact with the expanding section of the inner surface of the stator, one end of the extension discharge outlet is communicated with the fluid discharge outlet in the pump shell, the other end of the extension discharge outlet is communicated with the working cavity in contact with the reducing section of the inner surface of the stator, and the extension discharge outlet and the extension suction inlet are circumferentially separated and cannot be communicated with the same working cavity at the same time.

Fig. 28 and 29 show a right end cap 5-1 adopted in the present embodiment, in which: an extended suction inlet I95 with an included angle alpha 4, an extended discharge outlet I96 with an included angle alpha 5 and an auxiliary channel I80 which is communicated with the extended discharge outlet and has an included angle alpha 6, and the liquid distribution path, the circumferential position, the radial position and the shape of the auxiliary channel I are consistent with those of the left end cover. (the angles of the included angles of the extended suction port alpha 4, the extended discharge port alpha 5 and the auxiliary channel alpha 3 can be adjusted appropriately according to the experience of the professional engineer)

Referring to fig. 34 and 35, fig. 9 and 10 show a rotor 3 used in this embodiment, which includes an inner bore bushing 3-1, wherein a chamfer of 1 × 45 ° is provided between a radial outer surface of the rotor and two end faces of the rotor, 9 vane grooves 39 are provided in the rotor, a pin hole 711 is provided in the center of the bottom of each vane groove in the axial direction, a pin 71 is provided in the pin hole, two another pin holes 721 having the same radial area are symmetrically provided on both sides of the pin hole in the axial direction, another pin 72 is provided in the another pin hole, a bottom chamber front balancing passage 31 is provided between a front working chamber of the vane and a bottom chamber where the vane is located, so that the corresponding bottom chamber becomes an extension end of the front working chamber, an annular passage 7121 communicating the bottom chambers of the pins is provided in the rotor, three oblique passage 7122 for obtaining high-pressure working fluid are provided between the annular passage and two end faces of the rotor in the axial direction, the annular passage and the oblique passage constitute a pin bottom chamber fluid distribution passage 712, the oblique passage communicates with at least one of the left and right auxiliary working chamber 80 in the rotor, and the auxiliary working chamber.

FIG. 36 is a schematic view showing the main liquid distribution paths of the tank bottom chamber and the bottom chamber of another pin in this embodiment;

the other structural arrangements of this embodiment are the same as those of embodiment 1, and this embodiment replaces the description of the extended suction port 93, the extended discharge port 94 and the auxiliary passage 79 in embodiment 1 with the extended suction port one 95, the extended discharge port one 96 and the auxiliary passage one 80, and the rest is the same as that described in embodiment 1.

Embodiment 3, referring to fig. 1, 2, 3, 4, 5, 6, 9, 10, 11, and 12, fig. 37 to 54, this embodiment is a double-acting hydraulic vane pump, which mainly includes: the left pump casing 1, the stator 2, the rotor 3, the blades 4, the left end cover 5, the right end cover 5-1, the pin 71, the other pin 72, the right pump casing 1-1 and the transmission shaft 10.

The present example employed the stator, left end cap and right end cap described in example 1.

The structure of other main parts adopted by the pump is described in detail in the following description by referring to the attached drawings;

fig. 37 and 38, and fig. 9 and 10 show a rotor 3 used in this embodiment, the rotor includes an inner bore bushing 3-1, a chamfer of 1 × 45 ° is provided between the radial outer surface and the two ends of the rotor, 10 vane grooves 39 are provided in the rotor, a pin hole 711 is provided in the center of the bottom of each vane groove in the axial direction, a pin 71 is provided in the pin hole, two other pin holes 721 having the same radial area are symmetrically provided on the two sides of the pin hole in the axial direction, another pin 72 is provided in the other pin hole, a first slot bottom chamber rear balancing channel 32 is provided between the rear working chamber of the vane and the slot bottom chamber where the vane is located, so that the corresponding slot bottom chamber becomes the extension end of the rear working chamber, an annular channel 7121 communicating with each pin bottom chamber is provided in the rotor, three inclined hole channels 7122 capable of obtaining high-pressure working fluid are provided between the annular channel and the two end faces of the rotor in the axial direction, the annular channel and the inclined hole channels constitute a pin chamber fluid distribution channel 712, the inclined channel is provided in the radial position of the rotor at least one of the left and right end cover in the auxiliary working chamber, and the auxiliary working chamber 79, and at least one of the auxiliary working chamber is communicated with the left end cover 79.

Fig. 47 and 48 show an alternative pin 72 according to the present embodiment, which has a centrally located spring hole at the end of the pin, and a small hole at the radially outer end of the spring hole, which is smaller than the spring hole and extends through the head of the pin, and which is loaded by the spring only to couple the pin to the corresponding blade.

Each working cavity which contacts with the extending suction inlet 93 and contacts with the stator inner surface diameter expansion section guides suction pressure working fluid into the cavity from the outside of the pump when the volume is increased, each working cavity which contacts with the extending discharge outlet 94 and contacts with the stator inner surface diameter expansion section discharges discharge pressure working fluid out of the cavity when the volume is decreased, and the working fluid pressure in each working cavity has the characteristic of section change; the rear side balance channels 32 of each slot bottom cavity enable the working fluid pressure in the corresponding rear side working cavity to determine the working fluid pressure in the corresponding slot bottom cavity;

a difference value H generated by reducing the radius R of the large arc curved surface of the stator by the radius R of the large arc curved surface is firstly taken, and then the difference value H is used as a comparison parameter in the following setting.

Referring to fig. 1, another two another pins and another two another pin holes are connected with the vane to form another two pin bottom cavities correspondingly; fig. 50, 51 and 52 show the main liquid distribution paths of a tank bottom cavity and another pin bottom cavity, fig. 53 is an enlarged view of a part I of fig. 51, fig. 54 is an enlarged view of a part II of fig. 51, the vane shown in fig. 53 and 54 and another pin connected with the vane are positioned at the maximum radial position, the vane in the figure is taken as a front vane of a rear working cavity, and another pin bottom cavity rear intermittent liquid distribution channel II 0173 is arranged between the another pin bottom cavity and the rear working cavity in the corresponding part of the another pin and the vane; the blade in the figure is taken as a rear blade of the front working cavity, and another pin bottom cavity front side intermittent liquid distribution channel II 0174 is arranged between the other pin bottom cavity and the front working cavity in the corresponding part of the other pin and the blade.

According to the illustration of fig. 42, 51 and 53, another pin bottom cavity back side intermittent liquid distribution channel two 0173 and another pin bottom cavity front side intermittent liquid distribution channel two 0174 are arranged in the two common channels 74 of the blade:

two blind holes are respectively arranged at the lower part of the blade corresponding to the positions of the small holes on the pin spring hole, two circumferential through holes are axially arranged in the blade in a separating way, the through holes are positioned in the blade groove, the radial edge of each through hole is separated from the boundary line 003 of the blade groove and the radial outer surface of the rotor by about 1/2H, the through holes are respectively communicated with the blind holes at the lower part of the blade, and the small holes on the pin spring hole, the blind holes at the lower part of the blade and the through holes form two common channels 74 of another pin bottom cavity rear side intermittent liquid distribution channel 0173 and another pin bottom cavity front side intermittent liquid distribution channel 0174.

According to the illustration of fig. 51 and 54, another arrangement of the second pin bottom cavity rear intermittent liquid distribution channel 0173 is as follows:

a virtual boundary line after the intersection boundary line 002 of the rear side surface of the blade groove and the curved surface of the bottom of the blade groove is radially shifted to the outer diameter by about 1/5H is used as a radial starting boundary of the two blade parts 01731 of the other pin bottom cavity rear intermittent liquid distribution channel, a virtual boundary line after the intersection boundary line 003 of the rear side surface of the blade groove and the rotor radial outer surface is radially shifted to the inner diameter by about 4/15H is used as a radial ending boundary of the two blade parts 01731 of the other pin bottom cavity rear intermittent liquid distribution channel, and the two blade parts 01731 of the other pin bottom cavity rear intermittent liquid distribution channel is axially centered and slotted.

The common channel 74 and another two-blade part 01731 of the pin bottom cavity back side intermittent liquid distribution channel form another pin bottom cavity back side intermittent liquid distribution channel two 0173, and the other pin bottom cavity back side intermittent liquid distribution channel two 0173 utilizes the radial expansion displacement of the corresponding blade and another pin connected with the blade in work to regulate the connection and disconnection of the back side working cavity and the corresponding other pin bottom cavity under the coordination of the following back side balance chamber two 043.

According to the illustration of fig. 51 and 54, another pin bottom cavity front side intermittent liquid distribution channel II 0174 is arranged:

the virtual boundary line after the intersection boundary line 004 between the front side surface of the blade groove and the radial outer surface of the rotor is radially displaced to the outer diameter by about 3/5H is used as the radial starting boundary of the other two blade parts 01741 of the intermittent liquid distribution channel at the front side of the bottom cavity of the pin, the virtual boundary line after the intersection boundary line 004 is radially displaced to the inner diameter by about 21/10H is used as the radial ending boundary of the channel of the blade parts, and the other two blade parts 01741 of the intermittent liquid distribution channel at the front side of the bottom cavity of the pin is axially centered in a slotted mode.

The common channel 74 and another two-blade part 01741 of the intermittent liquid distribution channel at the front side of the bottom cavity of the pin form another intermittent liquid distribution channel II 0174 at the front side of the bottom cavity of the pin, and the other intermittent liquid distribution channel II 0174 at the front side of the bottom cavity of the pin regulates and controls the connection and disconnection of the working cavity at the front side and the bottom cavity of the pin correspondingly by utilizing the radial telescopic displacement of the corresponding blade and another pin connected with the blade in the working process under the coordination of the front side balance chamber II 044. (the cross-sectional area and radial position of the other pin bottom cavity front side intermittent liquid distribution channel II and the other pin bottom cavity rear side intermittent liquid distribution channel II can be properly adjusted according to the experience of professional engineers)

Referring to fig. 51 and 52, in this embodiment, the pressure of the front side surface of the vane contacting the high-pressure working fluid and the fluid flow film corresponds to the rear side compression force of the vane slot corresponding to the working condition that the vane is located at the maximum radial position and the front side working chamber of the vane contains the high-pressure working fluid and the rear side working chamber contains the low-pressure working fluid; and the pressure of the rear side surface of the blade contacting the high-pressure working liquid correspondingly forms the front pressing force of the blade groove.

39, 41, 42, 44, 45, 46, in correspondence with the operating conditions described for the rear side compression force constituting the vane slot, a rear side balancing chamber two 043 is provided on the rear side surface of the vane in the corresponding fitting surface, whose upper radial end boundary is smaller than the maximum radial boundary of the corresponding fitting surface by about 4/15H, whose both axial end boundaries are smaller than the both axial end boundaries of the corresponding fitting surface by about 1/3H, respectively, and whose lower radial end boundaries are larger at both axial end portions than the minimum radial boundary of the corresponding fitting surface by about 2/3H, respectively, and extend to the respective axial sides of the above-mentioned another pin bottom cavity rear side intermittent liquid distribution passage two 0173. Corresponding to the working condition of the front side compression force of the blade groove, a front side balance chamber II 044 is arranged on the front side surface of the blade in the corresponding matching surface, the radial upper end boundary of the front side balance chamber II 04is about 6/15H smaller than the maximum radial boundary of the corresponding matching surface, the axial two end boundaries of the front side balance chamber II 04are respectively about 1/3H smaller than the axial two end boundaries of the corresponding matching surface, the radial lower end boundaries of the front side balance chamber II 04are respectively about 2/3H larger than the minimum radial boundary of the corresponding matching surface at the two axial end parts and respectively extend to about 4/5H, and the middle residual part is about 4/15H larger than the minimum radial boundary of the corresponding matching surface.

The area of the front balance chamber II 044 comprises the area of another pin bottom cavity front intermittent liquid distribution channel II 0174, and the area of the rear balance chamber II 043 comprises the area of another pin bottom cavity rear intermittent liquid distribution channel II 0173; in any working condition, the front side balance chamber II and the rear side balance chamber II are communicated with each other through a circumferential through hole in the blade in the common channel 74 in the intermittent liquid distribution channels at the rear side and the front side of the other pin bottom cavity, and the rear side balance chamber II is combined with the front side balance chamber II to adjust the rear side pressing force of the blade groove and the front side pressing force of the blade groove.

A rear side liquid distribution channel II 0403 is respectively arranged between the rear side surface of the blade and the rear working cavity of the blade at two lower end parts axially separated in the rear side surface of the blade in the reserved rear side matching surface and the rear working cavity of the blade corresponding to the rear side balancing chamber II 043, the maximum radial boundary of the rear side liquid distribution channel in the setting is level with the intersecting boundary line of the rear side surface of the blade groove and the radial outer surface of the rotor, the rear side liquid distribution channel II enables the rear side plane of the blade positioned on the maximum radial position to be contacted with low-pressure working liquid through chamfers at two axial ends of the radial outer surface of the rotor, the working condition of rear side pressure of the regulated and controlled blade groove is correspondingly formed, the radial distribution of the rear side pressure of the regulated and controlled blade groove is reasonably corrected, and the attaching trend between the rear side surface of the blade in the rest part of the rear side balancing chamber II in the corresponding matching surface and the rear side surface of the blade groove is strengthened; (see fig. 41, 42, 46 and 49 for details) taking the boundary line 003 of the intersection of the rear side surface of the vane slot and the radial outer surface of the rotor as the supporting line of the rear side pressing force of the vane slot (see fig. 54), in this embodiment, the moment of the pressing force acting on the radial inner end of the supporting line is larger than the moment of the outer end of the supporting line, so that the rest of the rear balancing chamber two 043 in the corresponding matching surface is used as a rear side low-pressure joint surface, thereby the vane in the working condition performs working displacement in the corresponding joint and the rear balancing chamber two 043 is isolated from the rear working cavity (see the node 242 in fig. 51 for details).

A front side liquid distribution channel II 0404 is respectively arranged between the rear side surface of the blade at two lower end parts axially separated in the front side surface of the blade in the reserved front side matching surface and the front side working cavity of the blade corresponding to the front side matching surface of the front side balancing chamber II 044, the maximum radial boundary of the front side liquid distribution channel in the setting is level with the intersecting boundary line of the front side surface of the blade groove and the radial outer surface of the rotor, the front side liquid distribution channel II enables the front side plane of the blade positioned at the minimum radial position to be contacted with low-pressure working liquid through chamfers at the two axial ends of the radial outer surface of the rotor, and correspondingly forms the working condition of regulating and controlling the front side pressing force of the rear blade groove, so that the radial distribution of the regulated and controlled front side pressing force of the blade groove is reasonably corrected, and the attaching trend is strengthened between the front side surface of the blade in the rest part of the front side balancing chamber II in the corresponding matching surface and the front side surface of the blade groove; (see fig. 39, 43, 45 and 49 for details) taking a boundary line 004 of the intersection of the front side surface of the vane slot and the radial outer surface of the rotor as a supporting line (refer to fig. 54) of the front side pressing force of the vane slot, in the embodiment, the moment of the pressing force acting on the radial inner end of the supporting line is larger than the moment of the outer end of the supporting line, the remaining part of the front side balancing chamber two 044 in the corresponding matching surface is used as a front side low-pressure bonding surface, so that the vane in the working condition performs working displacement in the corresponding bonding, and the front side balancing chamber two 044 is separated from the front side working chamber at the maximum radial outer end and the axial two ends of the matching surface. (see node 244 in FIG. 52) (the depth of the chamber is about 2/15H, the depth of the chamber, the area of the chamber and the abutting surface can be adjusted according to the experience of the engineer)

As shown by 244 in fig. 52, in the operation of the vane corresponding to the front pressing force of the vane groove, the vane head rear portion, the remaining vane tail portion, the other kind of pin tail portion and the pin tail portion corresponding to the same vane are respectively contacted with the high-pressure working fluid by the extended discharge port, the other kind of pin bottom chamber rear intermittent fluid distribution channel two 0173, the groove bottom chamber rear balance channel one 32, the auxiliary channel and the pin bottom chamber fluid distribution channel, and the vane head front portion is contacted with the low-pressure working fluid by the extended suction port, and the radial area of the vane head front portion contacted with the low-pressure working fluid required for making the vane overcome the tendency of the front pressing force of the vane groove to expand outward is set first; as shown by point 242 in fig. 50, in the operation of the vane corresponding to the rear side pressing force of the vane groove, the extending discharge port, the second pin bottom chamber front side intermittent fluid distribution channel 0174, the auxiliary channel and the pin bottom chamber fluid distribution channel are respectively used for enabling the front side part of the vane head, the tail part of the pin and the tail part of the pin corresponding to the vane to be contacted with high-pressure working fluid, the extending suction port and the first groove bottom chamber rear side balance channel 32 are respectively used for enabling the rear side part of the vane head and the tail part of the residual vane corresponding to the vane to be contacted with low-pressure working fluid, and the total radial area of the pin and the pin corresponding to the vane is designed, part of the hydraulic force generated by the total radial area is used for balancing the hydraulic force generated by the front side part of the vane head, and the residual part of the hydraulic force is used for overcoming the rear side pressing force of the vane groove and keeping the vane to be stretched towards the outer diameter. The total radial area of the pin connected with the same blade and the other pin in the working condition is the total effective pressure area of the bottom of the blade. (the radial area of the leading part of the blade head, the radial area of the pin and the radial area of the other pin can be adjusted according to the experience of the professional engineer under the requirement of ensuring that the blade keeps proper contact stress with the inner surface of the stator in the whole working process)

Referring to fig. 45, 51 and 52, the corresponding major ways of obtaining liquid distribution from the slot bottom cavity 89, the pin bottom cavity and the other pin bottom cavity when the blade head contacts different circumferential nodes with the inner surface of the stator are shown, and correspondingly, the comparison between the hydraulic force obtained by the pin tail, the other pin tail and the residual blade tail to stretch the blade radially outward and the total hydraulic force obtained by each part of the blade head to retract the blade radially inward is shown:

in operation, as shown in point 241 in fig. 50, the front and rear working cavities of the blade are simultaneously communicated with the extension suction inlet, the corresponding bottom cavity of the blade is communicated with the rear working cavity through the first slot bottom cavity rear side balance channel 32, the other pin bottom cavity is communicated with the front working cavity through the second pin bottom cavity front side intermittent liquid distribution channel 0174 and is communicated with the rear working cavity through the second pin bottom cavity rear side intermittent liquid distribution channel 0173, and the pin bottom cavity is communicated with the extension discharge outlet through the auxiliary channel and the pin bottom cavity liquid distribution channel; the front part of the blade head, the rear part of the blade head, the tail of the residual blade and the tail of another pin which correspond to the blade are all contacted with low-pressure working fluid P1, the tail of the pin is contacted with high-pressure working fluid P2, and the pin pushes the blade to keep the outward diameter expansion trend by proper hydraulic force generated by the contact of the tail of the pin and the high-pressure working fluid;

at point 242 in fig. 51, the blade front working chamber communicates with the extension exhaust port, the rear working chamber remains to communicate with the extension suction port, the corresponding slot bottom chamber communicates with the rear working chamber through the slot bottom chamber rear balancing channel one 32, the other pin bottom chamber communicates with the front working chamber through the other pin bottom chamber front intermittent liquid distribution channel two 0174, and the pin bottom chamber communicates with the extension exhaust port through the auxiliary channel and the pin bottom chamber liquid distribution channel; the front part of the head of the blade, the tail of the pin and the tail of the other pin, which correspond to the blade, are all contacted with high-pressure working fluid P2, the rear part of the head of the blade and the tail of the rest blade are contacted with low-pressure working fluid P1, the sum of the radial area of the pin and the radial area of the other pin is larger than that of the front part of the head of the blade, and the blade is kept in the trend of extending to the outer diameter by proper hydraulic force generated by contacting the high-pressure working fluid with the tail of the pin and the tail of the other pin;

at point 243 in fig. 51, the front and rear working cavities of the vane are simultaneously communicated with the extended discharge port, the corresponding bottom cavity is communicated with the rear working cavity through the first slot bottom cavity rear side balance channel 32, the other pin bottom cavity is communicated with the front working cavity through the second pin bottom cavity front side intermittent liquid distribution channel 0174 and is communicated with the rear working cavity through the second pin bottom cavity rear side intermittent liquid distribution channel 0173, and the pin bottom cavity is communicated with the extended discharge port through the auxiliary channel and the pin bottom cavity liquid distribution channel; the front part of the blade head, the rear part of the blade head, the tail of the residual blade, the tail of the pin and the tail of the other pin which correspond to the blade are all contacted with high-pressure working fluid P2, and the radial position of the blade is limited by a reducing section of the inner surface of the stator;

at 244 in fig. 52, the blade rear working chamber is communicated with the extended exhaust port, the front working chamber is communicated with the extended suction port, the corresponding tank bottom chamber is communicated with the rear working chamber through a tank bottom chamber rear balance channel I32, the other pin bottom chamber is communicated with the rear working chamber through another pin bottom chamber rear intermittent liquid distribution channel II 0173, and the pin bottom chamber is communicated with the extended exhaust port through the auxiliary channel and the pin bottom chamber liquid distribution channel; the front part of the head of the blade is contacted with low-pressure working fluid P1, the tail of another pin, the tail of the pin, the rear part of the head of the blade and the tail of the residual blade which correspond to the blade are contacted with high-pressure working fluid P2, and the blade keeps the stretching trend towards the outer diameter by proper hydraulic force generated by the contact of the tail of the pin, the tail of the other pin and the tail of the residual blade with the high-pressure working fluid;

when the blade works to the point 241, the next working cycle is started.

The rest corresponds to the description in example 1.

Embodiment 4, referring to fig. 1, 2, 3, 4, 5, 6, 9, 10, 11, 12, fig. 55 to 70, this embodiment is a double-acting hydraulic vane pump, which mainly comprises: the left pump casing 1, the stator 2, the rotor 3, the blades 4, the left end cover 5, the right end cover 5-1, the pin 71, the sub-blades 4-1, the right pump casing 1-1 and the transmission shaft 10.

The structure of other main parts adopted by the pump is described in detail in the following description with reference to the attached drawings:

fig. 55 and 56, and fig. 9 and 10 show a rotor 3 adopted in the present embodiment, the rotor includes an inner bore bushing 3-1, a chamfer of 1 × 45 ° is provided between the radial outer surface of the rotor and both end faces of the rotor, 10 vane slots 39 are provided in the rotor, a pin hole 711 is provided in the center of the bottom of each vane slot in the axial direction, a pin 71 is provided in the pin hole, a slot bottom cavity rear side balance channel two 33 is provided between the rear side working cavity of the vane and the slot bottom cavity where the vane is located, so that the corresponding slot bottom cavity becomes the extension end of the rear side working cavity, an annular channel 7121 communicating with each pin bottom cavity is provided in the rotor, three inclined hole channels 7122 capable of obtaining high-pressure working fluid are respectively provided between the annular channel and both end faces of the rotor in the axial direction, and the annular channel and the inclined hole channels constitute a pin bottom cavity fluid distribution channel 712; the radial positions of the two ends of the inclined hole channels in the axial direction of the rotor correspond to the radial positions of the auxiliary channels 79 in the left end cover and the right end cover, and in operation, at least one inclined hole channel is communicated with one of the auxiliary channels in the left end cover and the right end cover, so that the bottom cavity of the pin always contains high-pressure working liquid.

FIGS. 57 to 64 show the embodiment using the vane 4, in which the axial position of the tail of the vane away from the pin hole of the center post of the rotor is symmetrically provided with two grooves 46 with the same radial area, and the vane is arranged in the vane groove of the rotor;

fig. 65, 66 and 70 show that the sub-blade 4-1 is adopted in the embodiment, the tail part of the sub-blade is provided with a circumferentially penetrating spring steel wire hole 491, a spring steel wire 49 is arranged in the spring steel wire hole, the spring steel wire is used for positioning the tail part of the sub-blade at the bottom of the groove bottom cavity, and the sub-blade is fully arranged in the groove at the bottom of the blade.

Referring to fig. 70, a vane intermediate chamber 489 is formed between the vane grooves, the vane grooves and the upper portion of the sub-vane.

Each working chamber which contacts with the extending suction port 93 and the stator inner surface diameter expansion section guides suction pressure working fluid into the chamber from the outside of the pump when the volume is increased, each working chamber which contacts with the extending discharge port 94 and the stator inner surface diameter expansion section discharges discharge pressure working fluid to the outside of the chamber when the volume is decreased, and the working fluid pressure in each working chamber has the characteristic of section change; the second rear side balance channels 34 of each tank bottom cavity enable the working fluid pressure in the corresponding rear side working cavity to determine the working fluid pressure in the corresponding tank bottom cavity;

See fig. 57, 59, 63, 64, the tail of the blade is provided with two grooves, two sub-blades are arranged in the grooves, and two middle cavities are correspondingly formed; fig. 68 and 69 show the main liquid distribution routes of the tank bottom cavity and the vane intermediate cavity, fig. 70 is an enlarged view of a part I of fig. 68, the vane shown in fig. 70 is positioned at the maximum radial position, the vane in the figure is used as a front vane of the rear working cavity, and an intermediate cavity rear intermittent liquid distribution channel one 0141 is respectively arranged in the corresponding parts of the vane and the rotor in the axial separation between the two vane intermediate cavity and the rear working cavity; the blade in the figure is taken as a rear blade of the front working cavity, and a middle cavity front intermittent liquid distribution channel I0142 is arranged between the two blade middle cavities and the front working cavity in the corresponding part of the blade in an axial separation way.

As shown in fig. 70, the first intermediate chamber rear intermittent liquid distribution channel 0141 is provided:

respectively taking a virtual boundary line after the intersecting boundary line 003 of the rear side surface of the blade groove and the radial outer surface of the rotor is radially displaced by about 4/15H as a radial starting boundary of a rotor part channel 01411 of two intermediate cavity rear side intermittent liquid distribution channels, respectively taking the virtual boundary line after the radially inner diameter displacement of the intersecting boundary line 003 line by about 22/15H as a radial ending boundary of the two rotor part channels, axially separating and opening a rotor part channel 01411 of the intermediate cavity rear side intermittent liquid distribution channel in a slotted mode, and axially separating and opening a blade head by taking the intersecting boundary line 003 of the rear side surface of the blade groove and the radial outer surface of the rotor as a radial starting boundary of a blade part channel 01412 of the two intermediate cavity rear side intermittent liquid distribution channels in a slotted mode;

the rotor part channel 01411 corresponds to the blade part channel 01412 in radial position and can be intermittently matched and communicated in work to form two groups of middle cavity rear side intermittent liquid distribution channels 0141, and the middle cavity rear side intermittent liquid distribution channels 0141 regulate and control the connection and disconnection of the rear side working cavity and the corresponding blade middle cavity by utilizing the radial expansion and contraction displacement of the corresponding blades.

As shown in fig. 70, the first intermediate chamber front intermittent liquid distribution channel 0142 is provided:

and virtual boundary lines after the boundary lines 004 of the intersection of the outer diameter surface of the rotor and the blades are radially displaced by about 11/15H are respectively used as radial initial boundary lines of two intermediate cavity front side intermittent liquid distribution channels 0142, the intermediate cavities are axially separated and opened in a slotted mode respectively, and the intermediate cavity front side intermittent liquid distribution channels 0142 utilize the radial telescopic displacement of the corresponding blades to regulate the connection and disconnection of the front side working cavity and the corresponding blade intermediate cavities. (the opening depth, the cross-sectional area and the radial position of the first intermediate cavity front side intermittent liquid distribution channel and the first intermediate cavity rear side intermittent liquid distribution channel can be properly adjusted according to the experience of professional engineers)

In this embodiment, see fig. 68 and 69, the pressure of the front side of the vane contacting the high-pressure working fluid and the fluid flow film corresponds to the back side pressing force of the vane slot corresponding to the condition that the vane is at the maximum radial position and the front side working chamber of the vane contains the high-pressure working fluid and the low-pressure working fluid, and the pressure of the back side of the vane contacting the high-pressure working fluid corresponds to the front side pressing force of the vane slot corresponding to the condition that the vane is at the minimum radial position and the back side working chamber of the vane contains the high-pressure working fluid and the front side working chamber contains the low-pressure working fluid.

57, 59, 60, 62, 63, 64, 68, 69, in correspondence with the working conditions described for the rear side pressing force of the vane slots, a rear side balancing chamber three 045 is provided on the rear side of the vane in the corresponding fitting surface, whose radially upper end boundary is smaller than the maximum radial boundary of the corresponding fitting surface by about 4/15H, whose axially both end boundaries are smaller than the axially both end boundaries of the corresponding fitting surface by about 1/3H, respectively, and whose radially lower end boundary is larger at both axial end portions than the minimum radial boundary of the corresponding fitting surface by about 2/3H and extends to the corresponding end surfaces of the vane grooves, respectively, and whose radially lower end boundary of the remaining portion between the two grooves of the vane is larger than the minimum radial boundary of the corresponding fitting surface by about 4/15H. Corresponding to the working condition of the front side compression force of the blade groove, a front side balance chamber three 046 is arranged on the front side surface of the blade in the corresponding matching surface, the radial upper end boundary of the front side balance chamber is smaller than the maximum radial boundary of the matching surface by about 4/15H, the axial two end boundaries of the front side balance chamber are respectively smaller than the axial two end boundaries of the corresponding matching surface by about 1/3H, the radial lower end boundaries of the front side balance chamber are respectively larger than the minimum radial boundary of the corresponding matching surface by about 2/3H at the axial two end parts and respectively extend towards each other by about 4/5H, and the radial lower end boundaries of the residual parts are larger than the minimum radial boundary of the corresponding matching surface by about 4/5H.

The area of the front balance chamber three 046 comprises the area of a middle cavity front intermittent liquid distribution channel one 0142, the area of the rear balance chamber three 045 comprises the area of a middle cavity rear intermittent liquid distribution channel one rotor part channel 01411, under any working condition, the front balance chamber three 046 and the rear balance chamber three 045 are communicated with each other through the blade middle cavity, and the rear balance chamber three is combined with the front balance chamber three for adjusting the rear pressing force of the blade groove and the front pressing force of the blade groove.

A rear side liquid distribution channel three 0405 is respectively arranged between the rear side surface of the blade and a rear side working cavity of the blade at two lower end parts axially separated in the rear side surface of the blade in the reserved rear side matching surface, the maximum radial boundary of the rear side liquid distribution channel in the setting is level with the intersecting boundary line of the rear side surface of the blade groove and the radial outer surface of the rotor, the rear side liquid distribution channel three enables the rear side plane of the blade positioned at the maximum radial position to be contacted with low-pressure working liquid through chamfers at the two axial ends of the radial outer surface of the rotor, the working condition of rear side pressure of the rear blade groove is correspondingly formed, the radial distribution of the rear side pressure of the blade groove after regulation is reasonably corrected, and the attaching trend between the rear side surface of the blade in the residual part of the rear side balancing chamber three in the corresponding matching surface and the rear side surface of the blade groove is strengthened; (see fig. 59, 61, 64 and 67 for details), the boundary 003 between the rear side of the vane slot and the radial outer surface of the rotor is taken as the supporting line of the rear pressing force of the vane slot (see fig. 70), and in this embodiment, the moment of the pressing force acting on the radial inner end of the supporting line is greater than the moment of the outer end of the supporting line, so that the remaining part of the rear balancing chamber three 045 in the corresponding mating surface is used as a rear low-pressure mating surface, thereby the vane in the working condition is displaced in the corresponding mating, and the rear balancing chamber three 045 is isolated from the rear working chamber (see the node 242 in fig. 68 for details).

A front side liquid distribution channel three 0406 is respectively arranged between the rear side surface of two lower end part blades axially separated in the front side surface of the blade in the reserved front side matching surface and the front side working cavity of the blade corresponding to the front side matching surface of the front side balancing chamber three 046, the maximum radial boundary of the front side liquid distribution channel in the setting is level with the intersecting boundary line of the front side surface of the blade groove and the radial outer surface of the rotor, the front side liquid distribution channel three enables the front side plane of the blade positioned on the minimum radial position to be contacted with low-pressure working liquid through chamfers of the radial outer surface of the rotor at the two axial ends, and correspondingly forms the working condition of regulating and controlling the front side pressing force of the rear blade groove, so that the radial distribution of the regulated and controlled front side pressing force of the blade groove is reasonably corrected, and the attaching trend is strengthened between the front side surface of the blade in the rest part of the front side balancing chamber three in the corresponding matching surface and the front side surface of the blade groove; (see fig. 57, 61, 63, 67 for details), a boundary line 004 where the front side surface of the vane slot intersects with the radial outer surface of the rotor is taken as a supporting line of the front side pressing force of the vane slot (refer to fig. 67), in the embodiment, the moment of the pressing force acting on the radial inner end of the supporting line is larger than the moment of the radial outer end of the supporting line, so that the rest of the front side balancing chamber three 046 in the corresponding matching surface is used as a front side low-pressure jointing surface, thereby the vane in the working condition does working displacement in the corresponding jointing, and the front side balancing chamber three 046 is isolated from the front side working cavity. (see node 244 in FIG. 69 in detail) (the opening depth of the balance chamber is about 2/15H, and the opening depth of the balance chamber, the area of the balance chamber and the abutting surface can be adjusted according to the experience of professional engineers)

The radial area of the vane is reduced by the radial area of the vane connecting pin and the vane middle cavity to form the remaining area of the tail of the vane.

As shown at 244 in fig. 69, in the blade, during the operation corresponding to the pressing force on the front side of the blade groove, the extending discharge port, the first intermediate chamber rear intermittent fluid distribution passage 0141, the second tank bottom chamber rear balancing passage 33, the auxiliary passage and the pin bottom chamber fluid distribution passage are respectively used for contacting the blade head rear portion, the remaining blade tail portion, the blade intermediate chamber and the pin tail portion corresponding to the same blade with the high-pressure fluid, and the extending suction port is used for contacting the blade head front portion with the low-pressure fluid, and the radial areas of the blade head front portion contacting the low-pressure fluid required for the blade to overcome the tendency of the blade groove front pressing force to expand to the outer diameter are designed, and as shown at 242 in fig. 68, the extending discharge port, the first intermediate chamber front intermittent fluid distribution passage 0142, the auxiliary passage and the pin bottom chamber fluid distribution passage are designed for contacting the blade head front portion, the blade intermediate chamber and the pin tail portion corresponding to the blade in the operation corresponding to the pressing force on the rear side of the blade groove, the extending suction port, the second tank bottom chamber rear side balancing passage 33, and the auxiliary passage and the pin bottom chamber are respectively used for overcoming the tendency of the blade to generate the total blade head portion and the hydraulic pressure to generate the blade head portion and the hydraulic pressure of the blade. The total radial area of the blade middle cavity and the pin corresponding to the same blade in the working condition is the effective pressure bearing area of the bottom of the blade. (the radial area of the leading portion of the blade head, the radial area of the pin and the area of the vane intermediate chamber can be adjusted according to the experience of the expert engineer, with the aim of ensuring that the blade maintains a suitable contact stress with the internal surface of the stator throughout operation)

Referring to fig. 68 and 69, the main ways of obtaining the liquid distribution of the corresponding tank bottom cavity 89, pin bottom cavity and vane middle cavity when the vane head contacts different circumferential nodes with the inner surface of the stator are shown, and correspondingly, the comparison between the hydraulic force for extending the vane radially outward obtained by the pin tail, the vane middle cavity and the remaining vane tail and the total hydraulic force for retracting the vane radially inward obtained by each part of the vane head is shown:

in operation, as shown in point 241 in fig. 69, the front and rear working chambers of the vane are simultaneously communicated with the extension suction inlet, the corresponding bottom chamber of the vane is communicated with the rear working chamber through the rear balancing channel two 33 of the bottom chamber of the vane, the middle chamber of the vane is communicated with the front working chamber through the front intermittent liquid distribution channel one 0142 of the middle chamber and is communicated with the rear working chamber through the rear intermittent liquid distribution channel one 0141 of the middle chamber, and the bottom chamber of the pin is communicated with the extension discharge outlet through the auxiliary channel and the liquid distribution channel of the bottom chamber of the pin; the front part of the head of the blade, the rear part of the head of the blade, the tail of the residual blade and the middle cavity of the blade corresponding to the blade are all contacted with low-pressure working fluid P1, the tail of the pin is contacted with high-pressure working fluid P2, and the pin pushes the blade to keep the trend of extending to the outer diameter by proper hydraulic force generated by the high-pressure working fluid at the tail of the pin;

at point 242 in fig. 68, the blade front side working chamber communicates with the extension exhaust port, the rear side working chamber remains to communicate with the extension suction port, the corresponding tank bottom chamber communicates with the rear side working chamber through the tank bottom chamber rear side balancing channel two 33, the blade middle chamber communicates with the front side working chamber through the middle chamber front side intermittent liquid distribution channel one 0142, and the pintle bottom chamber communicates with the extension exhaust port through the auxiliary channel and the pintle bottom chamber liquid distribution channel; the front part of the head of the blade, the tail of the pin and the middle cavity of the blade corresponding to the blade are all contacted with high-pressure working fluid P2, the rear part of the head of the blade and the tail of the residual blade corresponding to the blade are contacted with low-pressure working fluid P1, the sum of the radial area of the pin and the radial area of the middle cavity of the blade is larger than that of the front part of the head of the blade, and the blade keeps the outward radial expansion trend by proper hydraulic force generated by the high-pressure working fluid contacted with the tail of the pin and the middle cavity of the blade;

at point 243 in fig. 68, the front and rear working chambers of the vane are simultaneously communicated with the extension outlet, the corresponding bottom chamber of the vane is communicated with the rear working chamber through the second rear balancing channel 33 of the bottom chamber of the vane, the middle chamber of the vane is communicated with the front working chamber through the first front intermittent liquid distribution channel 0142 of the middle chamber and is communicated with the rear working chamber through the first rear intermittent liquid distribution channel 0141 of the middle chamber, and the bottom chamber of the pin is communicated with the extension outlet through the auxiliary channel and the liquid distribution channel of the bottom chamber of the pin; the front part of the blade head, the rear part of the blade head, the tail part of the residual blade, the tail part of the pin and the middle cavity of the blade which correspond to the blade are all contacted with high-pressure working fluid P2, and the radial position of the blade is limited by a reducing section of the inner surface of the stator;

at 244 in fig. 69, the blade rear working chamber is communicated with the extended discharge port, the front working chamber is communicated with the extended suction port, the corresponding tank bottom chamber is communicated with the rear working chamber through a tank bottom chamber rear balance channel two 33, the blade middle chamber is communicated with the rear working chamber through a middle chamber rear intermittent liquid distribution channel one 0141, and the pin bottom chamber is communicated with the extended discharge port through an auxiliary channel and a pin bottom chamber liquid distribution channel; the front part of the head of the blade is contacted with low-pressure working fluid P1, the middle cavity of the blade, the tail part of the pin, the tail part of the residual blade and the rear part of the head of the blade which correspond to the blade are contacted with high-pressure working fluid P2, and the blade keeps the outward radial extension trend by proper hydraulic force generated by the high-pressure working fluid contacted with the tail part of the pin, the middle cavity of the blade and the tail part of the residual blade;

when the blade works to the point 241, the next working cycle is started.

The radial areas of the front part of the blade head, the rear part of the blade head, the pin and the blade middle cavity are the minimum radial areas which are respectively and correspondingly cut perpendicular to the radial axis of the corresponding blade groove;

in the whole action period, the first intermediate cavity front side intermittent liquid distribution channel 0142 is combined with the first intermediate cavity rear side intermittent liquid distribution channel 0141, so that the corresponding blade intermediate cavity can introduce suction pressure working liquid into the cavity through the corresponding working cavity in volume expansion, and the corresponding blade intermediate cavity can discharge pressure working liquid in the cavity to the outside of the pump through the corresponding working cavity in volume reduction, so that the working liquid flow generated by the blade intermediate cavity in the volume change process in operation is totally summarized into the calculated displacement of the pump, the volume efficiency of the hydraulic vane pump in the embodiment is improved, and the working pressure is also improved; the working fluid pressure in the corresponding blade middle cavity is determined by the circumferential position of the rear side working cavity and/or the front side working cavity communicated with the rear side working cavity and/or the front side working cavity on the inner surface of the stator, so that the corresponding blade middle cavity obtains optimized liquid distribution of sectional adjusting pressure, and the mechanical efficiency of the pump is improved.

In the whole action period, working cavities at the front side and the rear side of the blade contain working liquid with different pressures, and the corresponding groove bottom cavity contains high-pressure working liquid, wherein the sum of the radial area of a pin, the radial area of a middle cavity of the blade and the area of the tail part of the residual blade corresponding to the same blade is used as the effective pressure bearing area of the bottom of the blade; in the work that working cavities at the front side and the rear side of each blade contain working fluid with different pressures and a corresponding groove bottom cavity contains low-pressure working fluid, the sum of the radial area of a pin corresponding to the same blade and the radial area of a middle cavity of each blade is used as the effective pressure bearing area of the bottom of each blade; in the work that the working cavities on the front side and the rear side of the blade simultaneously contain low-pressure working fluid, the radial area of the pin is used as the effective pressure bearing area of the bottom of the blade; therefore, the contact stress formed by the blade head and the inner surface of the stator in different sections through hydraulic force is properly adjusted, and the working pressure of the pump is further improved.

This example is identical to that described in example 1, except as described in relation to the other column.

Embodiment 5, referring to fig. 1, 2, 9, 10, 28 to 33, and 57 to 66, see fig. 71 to 73, this embodiment is a single-acting hydraulic vane pump, which mainly includes: the left pump casing 1, the stator 2, the rotor 3, the blades 4, the left end cover 5, the right end cover 5-1, the pin 71, the sub-blades 4-1, the right pump casing 1-1 and the transmission shaft 10.

fig. 32 and 33 show the stator 2 used in the present embodiment, in which the inner surface of the stator is provided with: 1. the section is away from the axle center distance and increases the curved surface of hole enlargement section that becomes more continuously, a section is away from the reducing section curved surface that the axle center distance becomes less continuously, a section connects the curved surface of hole enlargement section and reducing section curved surface and uses R as the curved surface of radius, a section connects reducing section curved surface and the curved surface of hole enlargement section and uses R as the curved surface of radius.

Fig. 28 and 29 show a right end cap 5-1 adopted in the present embodiment, in which: an extended suction inlet I95 with an included angle alpha 4, an extended discharge outlet I96 with an included angle alpha 5 and an auxiliary channel I80 which is communicated with the extended discharge outlet and has an included angle alpha 6, and the liquid distribution path, the circumferential position, the radial position and the shape of the auxiliary channel I are consistent with those of the left end cover. (the angles of the included angles of the extended suction inlet alpha 4, the extended discharge outlet alpha 5 and the auxiliary channel alpha 3 can be adjusted according to the experience of professional engineers)

Referring to fig. 71 and 72, fig. 9 and 10 show a rotor 3 adopted in the present embodiment, the rotor includes an inner bore bushing 3-1, a chamfer of 1 × 45 ° is provided between the radial outer surface of the rotor and both end faces of the rotor, 9 vane grooves 39 are provided in the rotor, a pin hole 711 is provided in the center of the bottom of each vane groove in the axial direction, a pin 71 is provided in the pin hole, a groove bottom cavity rear side balance channel 32 is provided between the rear side working cavity of the vane and the groove bottom cavity where the vane is located, so that the corresponding groove bottom cavity becomes the outer extension end of the rear side working cavity, an annular channel 7121 communicating with each pin bottom cavity is provided in the rotor, three inclined bore channels 7122 capable of obtaining high pressure working fluid are respectively provided between the annular channel and both end faces in the axial direction of the rotor, the annular channel and the inclined bore channels constitute a pin bottom cavity fluid distribution channel 712, the inclined bore channels correspond to the radial positions of one of the auxiliary channels 80 in the left and right end covers in the axial direction of the rotor, in operation, at least one of the inclined bore channels communicates with one of the left and right end covers, so that the auxiliary channels always hold the high pressure working fluid.

FIG. 73 is a schematic view showing the main liquid distribution paths of the tank bottom chamber and the intermediate chamber in this embodiment;

the other structural arrangements of this embodiment are the same as those of embodiment 4, and this embodiment replaces the description of the extended suction inlet 93, the extended discharge outlet 94 and the auxiliary passage 79 in embodiment 4 with the extended suction inlet one 95, the extended discharge outlet one 96 and the auxiliary passage one 80, and the rest is the same as that described in embodiment 4.

Embodiment 6 referring to fig. 1, 2, 3, 4, 5, 6, 9, 10, 11, 12 fig. 74 to 86 this embodiment is a double-acting hydraulic vane pump, which mainly comprises: the left pump casing 1, the stator 2, the rotor 3, the blades 4, the left end cover 5, the right end cover 5-1, the pin 71, the right pump casing 1-1 and the transmission shaft 10.

The pump adopts other main part structures which are described in detail in the following description with reference to the attached drawings:

fig. 82 and 83, referring to fig. 9 and 10, show a rotor 3 adopted in the present embodiment, the rotor includes an inner bore bushing 3-1, a chamfer of 1 × 45 ° is provided between the radial outer surface of the rotor and both end faces of the rotor, 10 vane slots 39 are provided in the rotor, a spring hole 38 is provided in the axial center of the bottom of each vane slot, a spring 381 is provided in the spring hole, two pin holes 711 having the same radial area are symmetrically provided in the axial center of the bottom of each vane slot, a pin 71 is provided in each pin hole, an annular channel 7121 communicating with the bottom cavity of each pin is provided in the rotor, three inclined bore channels 7122 capable of obtaining high-pressure working fluid are provided between the annular channel and both end faces of the rotor in the axial direction, and the annular channel and the inclined bore channels constitute a pin bottom cavity fluid distribution channel 712; the radial positions of the two ends of the inclined hole channel in the axial direction of the rotor correspond to the radial positions of the auxiliary channels 79 in the left end cover and the right end cover, and in operation, at least one inclined hole channel is communicated with one of the auxiliary channels in the left end cover and the right end cover, so that the bottom cavity of the pin always contains high-pressure working liquid.

Fig. 74 to 81 show the vane 4 used in this embodiment, in which the two contact angles of the vane are at the minimum and maximum radial positions and there are two contact positions with the inner surface of the stator intermittently, the contact position of the rear side contact angle of the vane head at the maximum radial position corresponding to the rotation direction of the rotor is divided into the rear side portion of the vane head, the contact position of the front side contact angle of the vane head at the minimum radial position is divided into the front side portion of the vane head, and the vane head is divided into the remaining portions of the vane head except the rear side portion of the vane head and the front side portion of the vane head; the rest part of the blade head generates a front side clearance channel 46 between the rest part of the blade head and the front side working cavity in the work of contacting the diameter expanding section and separating the front side contact angle of the blade head from the inner surface of the stator, or generates a rear side clearance channel 45 between the rest part of the blade head and the rear side working cavity in the work of contacting the diameter reducing section and separating the rear side contact angle of the blade head from the inner surface of the stator (see the nodes 241 and 243 of fig. 83 in detail); a slot bottom cavity middle balance channel arranged at least in the blade between the rest part of the blade head and the slot bottom cavity where the blade is positioned; the balance channel in the middle of the groove bottom cavity enables hydraulic force for enabling the blade to radially displace not to be generated between the rest part of the head of the blade and the tail of the blade with the same radial area as the head of the blade, and the other part of the tail of the blade can generate hydraulic force for enabling the blade to radially extend outwards when the corresponding groove bottom cavity contains discharge pressure working fluid to be used as a hydraulic force action part of the bottom of the blade.

In the working period, each working cavity which contacts with the extension suction inlet 93 and the stator inner surface diameter expansion section guides suction pressure working fluid into the cavity from the outside of the pump when the volume is increased, each working cavity which contacts with the extension discharge outlet 94 and the stator inner surface diameter reduction section discharges discharge pressure working fluid to the outside of the cavity when the volume is reduced, and the working fluid pressure in each working cavity has the characteristic of sectional change;

Fig. 84, 85 show the main distribution paths of the slot bottom cavities, fig. 86 is an enlarged view of the portion I of fig. 84, the vane shown in fig. 86 is in the maximum radial position, and the vane in the figure is taken as the front vane of the rear working cavity, and a group of slot bottom cavity rear intermittent distribution channels 0131 are arranged between the corresponding slot bottom cavity and the rear working cavity in the corresponding part of the vane and the rotor which are axially centered; the vane in the figure is taken as the rear vane of the front working chamber, and a front intermittent liquid distribution channel 0132 of the slot bottom chamber is arranged between the corresponding slot bottom chamber and the front working chamber in the corresponding part axially centered on the vane.

Fig. 86, arrangement of the tank bottom cavity rear intermittent liquid distribution channel 0131:

taking an intersecting boundary line 003 of the rear side surface of the blade groove and the radial outer surface of the rotor, which is subjected to radial displacement of about 4/15H, as a radial starting boundary of a rotor part channel 01311 of an intermittent liquid distribution channel at the rear side of a groove bottom cavity, radially and inwardly extending to about 1 to 3/5H in a slotted mode, taking the intersecting boundary line 003 as a radial starting boundary of an upper end channel 01312 of the blade part of the intermittent liquid distribution channel at the rear side of the groove bottom cavity and opening a blade head in a slotted mode, and taking a virtual boundary line after the intersecting boundary line 003 is radially and inwardly displaced by about 4/15H as a radial starting boundary of a lower end channel 01313 of the blade part of the intermittent liquid distribution channel at the rear side of the groove bottom cavity and opening to the tail of the blade in a slotted mode;

axial positions of the rotor part channel 01311, the blade part upper end channel 01312 and the blade part lower end channel 01313 correspond to each other, and the rotor part channel, the blade part upper end channel 3242 zxft 4736 and the blade part lower end channel 01313 can be intermittently communicated with each other in work to form a groove bottom cavity rear side intermittent liquid distribution channel 0131, and the groove bottom cavity rear side intermittent liquid distribution channel 0131 utilizes radial telescopic displacement of corresponding blades to regulate and control communication and disconnection between a rear side working cavity and a corresponding groove bottom cavity.

Fig. 86, arrangement of the intermittent liquid distribution channel 0132 at the front side of the groove bottom cavity:

taking a virtual boundary line after an intersecting boundary line 004 between the front side surface of the blade groove and the radial outer surface of the rotor is shifted to the outer diameter by about 11/15H as a radial starting boundary of an intermittent liquid distribution channel 0132 at the front side of a groove bottom cavity, and opening the blade tail in a slotted mode in the axial centering; the intermittent liquid distribution channel 0132 at the front side of the tank bottom cavity regulates and controls the connection and disconnection of the front side working cavity and the corresponding tank bottom cavity by utilizing the radial expansion and contraction displacement of the corresponding blade. (the opening depth, the cross-sectional area and the radial position of the tank bottom cavity front side intermittent liquid distribution channel and the tank bottom cavity rear side intermittent liquid distribution channel can be properly adjusted according to the experience of professional engineers)

Referring to fig. 84 and 85, in this embodiment, the vane is located at the maximum radial position, the front working chamber of the vane contains the high-pressure working fluid, and the rear working chamber of the vane contains the low-pressure working fluid, the pressure of the front side of the vane contacting the high-pressure working fluid corresponds to the rear pressing force of the vane slot, and the pressure of the rear side of the vane contacting the high-pressure working fluid corresponds to the front pressing force of the vane slot corresponding to the condition that the vane is located at the minimum radial position, the rear working chamber of the vane contains the high-pressure working fluid, and the front working chamber contains the low-pressure working fluid.

As shown in fig. 74 to 85, in response to the working condition of the rear side compression force of the blade groove, rear side balance chambers four 047 are respectively arranged on the rear side surface of the blade and the rear side surface of the blade groove in the corresponding matching surfaces, the radial upper end boundary of the rear side balance chamber four 047-2 of the rotor part is smaller than the maximum radial boundary of the corresponding matching surface by about 4/15H, the axial two end boundaries thereof are respectively smaller than the axial two end boundaries of the corresponding matching surfaces by about 1 and 2/3H, and the radial lower end thereof opens the corresponding groove bottom cavity; the radial upper end boundary of the blade part rear side balance chamber four 047-1 is smaller than the maximum radial boundary of the corresponding matching surface by about 4/15H, the axial two-end boundaries of the blade part rear side balance chamber are respectively smaller than the axial two-end boundaries of the corresponding matching surface by about 1/3H, the radial lower end boundary of the blade part rear side balance chamber four 047-1 is larger than the axial two-end boundaries of the corresponding matching surface by about 1 and 1/3H at the axial two-end parts, and respectively extends by about 1 and 2/3H in opposite directions, and the radial lower end of the residual part opens the blade tail; the rotor part rear side balancing chamber four 047-2 and the blade part rear side balancing chamber four 047-1 form a rear side balancing chamber four 047.

Correspondingly forming the working condition of the front side compression force of the blade groove, respectively arranging a front side balance chamber four 048 on the front side surface of the blade and the front side surface of the blade groove in the corresponding matching surface, wherein the radial upper end boundary of the front side balance chamber four 048-2 of the rotor part is less than the maximum radial boundary of the corresponding matching surface by about 4/15H, the axial two-end boundaries of the rotor part are respectively less than the axial two-end boundaries of the corresponding matching surface by about 1H, and the radial lower end of the rotor part is provided with a corresponding groove bottom cavity; the radial upper end boundary of the vane part front side balance chamber four 048-1 is less than the maximum radial boundary of the corresponding matching surface by about 4/15H, the axial two-end boundary thereof is respectively less than the axial two-end boundary of the corresponding matching surface by about 1/3H, the radial lower end boundary of the blade is larger than the minimum radial boundary of the corresponding matching surface by about 2/3H at two axial end parts, the radial lower end of the radial lower end boundary extends by about 1H stop in opposite directions, and the radial lower end of the middle residual part is provided with a blade tail part; the rotor section front side balance chamber four 048-2 and the vane section front side balance chamber four 048-1 constitute a front side balance chamber four 048.

The area of the front side balance chamber four contains the area of a groove bottom cavity front side intermittent liquid distribution channel 0132, the area of the rear side balance chamber four contains the areas of a blade lower end part channel 01314 and a rotor lower end channel 01312 of the groove bottom cavity rear side intermittent liquid distribution channel, in any working condition, the front side balance chamber four and the rear side balance chamber four are communicated with each other through the groove bottom cavity, and the rear side balance chamber four is combined with the front side balance chamber four to be used for adjusting blade groove rear side pressing force and blade groove front side pressing force.

Corresponding to the rear side matching surface reserved in the rear side balancing chamber four 047, rear side liquid distribution channels four 0407-1 are respectively arranged in the blade between the two lower part blade rear side surfaces axially separated in the blade rear side surface in the reserved rear side matching surface and the rear side working cavity of the blade, the maximum radial boundary of the rear side liquid distribution channel of the blade part in the arrangement is leveled with the intersection boundary line of the blade groove rear side surface and the rotor radial outer surface, rear side liquid distribution channels four 0407-2 are respectively arranged in the rotor between the two part blade rear side surfaces axially separated in the blade groove rear side surface in the reserved rear side matching surface and the rear side working cavity of the blade, the minimum radial boundary of the rotor part rear side liquid distribution channel I leaves the intersection boundary line of the blade groove rear side surface and the rotor radial outer surface by about 2/3H, the axial positions of a blade part rear side liquid distribution channel four 0407-1 and a rotor part rear side liquid distribution channel four 0407-2 are corresponding and can be intermittently communicated with each other, the blade part rear side liquid distribution channel four 0407-1 and the rotor part rear side liquid distribution channel four 0407-2 form a rear side liquid distribution channel four 0407, the rear side liquid distribution channel four enables the rear side plane of the blade positioned at the maximum radial position to be contacted with low-pressure working liquid through chamfers at the two axial ends of the radial outer surface of the rotor, the working condition of rear blade groove rear side pressure regulation and control is correspondingly formed, the radial distribution of the regulated and controlled blade groove rear side pressure is reasonably corrected, and therefore the attaching trend between the blade rear side surface and the blade groove rear side surface in the rest part of the rear side balance chamber four in the corresponding matching surface is strengthened; (see fig. 76, 78, 79, 81, with reference to fig. 24 for details), taking the boundary 003 between the intersection of the rear side of the vane slot and the radially outer surface of the rotor as the support line for the above-mentioned rear side pressing force of the vane slot (see fig. 86), in this embodiment, the moment of the pressing force acting on the radially inner end of the support line is greater than the moment of the outer end of the support line, so that the remaining portion of the rear balancing chamber four 047 in the corresponding mating surface serves as a rear side low pressure abutment surface, thereby allowing the vane in this condition to perform working displacement in the corresponding abutment and isolating the rear balancing chamber four 047 from the rear working chamber at the largest radially outer and axial ends of the mating surface (see node 242 in fig. 84 for details).

A front side liquid distribution channel four 0408 is arranged between the rear side surface of the blade and the front side working cavity of the blade at two lower end parts axially separated in the front side surface of the blade in the reserved front side matching surface, corresponding to the front side matching surface reserved by the front side balancing chamber four 048, the maximum radial boundary of the front side liquid distribution channel in the setting is level with the intersection boundary line of the front side surface of the blade groove and the radial outer surface of the rotor, the front side liquid distribution channel four enables the front side plane of the blade positioned at the minimum radial position to be contacted with low-pressure working liquid through chamfers at the two axial ends of the radial outer surface of the rotor, and correspondingly forms the working condition of regulating and controlling the front side pressing force of the rear blade groove, so that the radial distribution of the regulated and controlled front side pressing force of the blade groove is reasonably corrected, and the attaching trend between the front side surface of the blade in the residual part of the front side balancing chamber four in the corresponding matching surface and the front side surface of the blade groove is strengthened; (see fig. 74, 78, 79, 80, refer to fig. 24. In this embodiment, the moment of the pressing force acting on the radially inner end of the supporting line is greater than the moment of the outer end of the supporting line, and the remaining part of the front balancing chamber four 048 in the corresponding mating surface is used as a front low-pressure mating surface, so that the working displacement of the vane in the corresponding mating condition is realized, and the maximum radial outer end and axial both ends of the front balancing chamber four 048 in the mating surface are isolated from the front working chamber. (see the 244 nodes in FIG. 85 in detail) (the opening depth of the balance chamber is about 2/15H, and the opening depth of the balance chamber, the area of the balance chamber and the abutting surface can be adjusted according to the experience of the professional engineer)

The radial area of the blade minus the radial area of the blade connecting pin is the residual area of the tail of the blade;

as shown at 242 in fig. 84, in the blade, in the operation corresponding to the pressing force on the rear side of the blade groove, the discharge port, the groove bottom cavity intermediate balance passage, the groove bottom cavity front intermittent distribution passage 0132, the auxiliary passage and the pin bottom cavity distribution passage are extended, the blade head front side portion, the remaining blade tail portion and the pin tail portion corresponding to the same blade are respectively contacted with the high-pressure working fluid P2, the suction port is extended to contact the low-pressure working fluid P1 with the blade head rear side portion, the radial area of the blade head rear side portion contacted with the low-pressure working fluid required for the blade to overcome the tendency of the blade groove rear side pressing force to expand outward is designed, as shown at 244 in fig. 85, the discharge port, the groove bottom cavity intermediate balance passage, the groove bottom cavity rear intermittent distribution passage 0131, the auxiliary passage and the pin bottom cavity distribution passage are extended in the operation corresponding to the pressing force on the front side of the blade, the discharge port, the remaining blade head rear side portion, the remaining blade tail portion and the pin tail portion are contacted with the low-pressure working fluid P2, and the blade head portion contacted with the low-pressure working fluid P1 required for the blade to overcome the tendency of the blade groove front side pressing force to contact. (the radial area of the back part of the blade head, the radial area of the front part of the blade head and the radial area of the pin can be adjusted according to the experience of professional engineers under the requirement of ensuring that the blade keeps proper contact stress with the inner surface of the stator in the whole working process)

See fig. 84 and 85, showing the corresponding groove bottom cavity 89 when the blade head contacts different circumferential nodes with the inner surface of the stator, the pin bottom cavity obtaining the main way of liquid distribution, correspondingly, showing the comparison of the hydraulic force obtained by the pin tail and the residual blade tail to make the blade stretch outward and the total hydraulic force obtained by each part of the blade head to make the blade retract inward:

in operation, as shown in point 241 in fig. 84, the front and rear working cavities of the vane are simultaneously communicated with the extension suction inlet, the corresponding groove bottom cavity is communicated with the front working cavity at least through the front clearance channel 46 and the middle balance channel of the groove bottom cavity, and the pin bottom cavity is communicated with the extension discharge outlet through the auxiliary channel and the pin bottom cavity liquid distribution channel; the front part of the blade head, the rest part of the blade head, the rear part of the blade head and the tail part of the residual blade corresponding to the blade are all contacted with low-pressure working fluid P1, the tail part of the pin is contacted with high-pressure working fluid P2, and the pin pushes the blade to keep the outward diameter expansion trend by proper hydraulic force generated by the high-pressure working fluid at the tail part of the pin;

at point 242 in fig. 84, the front working chamber of the vane communicates with the extended exhaust port, the rear working chamber remains in communication with the extended intake port, the corresponding tank bottom chamber communicates with the front working chamber through the tank bottom chamber front intermittent liquid distribution channel 0132, the rest of the head of the vane communicates with the corresponding tank bottom chamber through the tank bottom chamber middle balance channel, and the pin bottom chamber communicates with the extended exhaust port through the auxiliary channel and the pin bottom chamber liquid distribution channel; the front part of the blade head, the rest part of the blade head, the residual blade tail and the pin tail corresponding to the blade are all contacted with high-pressure working fluid P2, the rear part of the blade head is contacted with low-pressure working fluid P1, and the blade keeps the outward diameter stretching trend by proper hydraulic force generated by the high-pressure working fluid contacted with the pin tail and the action part at the bottom of the blade;

at point 243 in fig. 84, the front and rear working chambers of the vane are simultaneously communicated with the extension outlet, the corresponding tank bottom chamber is communicated with the rear working chamber at least through the rear clearance channel 45 and the middle balance channel of the tank bottom chamber, and the pin bottom chamber is communicated with the extension outlet through the auxiliary channel and the pin bottom chamber liquid distribution channel; the front part of the blade head, the rest part of the blade head, the rear part of the blade head, the tail part of the residual blade and the tail part of the pin, which correspond to the blade, are all contacted with high-pressure working fluid P2, and the radial position of the blade is limited by a reducing section of the inner surface of the stator;

at 244 in fig. 85, the working cavity at the back side of the blade is communicated with the extended discharge port, the working cavity at the front side is communicated with the extended suction port, the corresponding cavity bottom is communicated with the working cavity at the back side through the intermittent liquid distribution channel 0131 at the back side of the cavity bottom, the rest part of the head of the blade is communicated with the corresponding cavity bottom through the middle balance channel of the cavity bottom, and the cavity bottom of the pin is communicated with the extended discharge port through the auxiliary channel and the liquid distribution channel of the cavity bottom of the pin; the front part of the head of the blade is contacted with low-pressure working fluid P1, the tail part of a pin, the tail part of the residual blade, the rear part of the head of the blade and the rest part of the head of the blade which correspond to the blade are contacted with high-pressure working fluid P2, and the blade keeps the trend of extending towards the outer diameter by proper hydraulic force generated by the high-pressure working fluid contacted with the tail part of the pin and the action part of the bottom of the blade;

when the blade works to the point 241, the next working cycle is started.

The radial areas of the front part of the blade head, the rear part of the blade head, the pin and the acting part of the blade bottom are the minimum radial areas which are respectively and correspondingly cut perpendicular to the radial axis of the corresponding blade groove;

in the whole action period, the middle balance channel of the tank bottom cavity is combined with the front side clearance channel or the rear side clearance channel, the rear side intermittent liquid distribution channel of the tank bottom cavity and the front side intermittent liquid distribution channel of the tank bottom cavity are combined, so that the corresponding tank bottom cavity can introduce suction pressure working liquid into the cavity through the corresponding working cavity in volume expansion, and the corresponding tank bottom cavity can discharge the pressure working liquid in the cavity to the outside of the pump through the corresponding working cavity in volume reduction, so that the working liquid flow generated in the volume change process of the tank bottom cavity in work is totally summarized into the calculated displacement of the pump, the volume efficiency of the hydraulic vane pump in the embodiment is improved, and the working pressure is also improved; the working liquid pressure in the corresponding tank bottom cavity is determined by the circumferential position of the rear side working cavity and/or the front side working cavity communicated with the tank bottom cavity on the inner surface of the stator, so that the optimized liquid distribution of the sectional adjusting pressure obtained by the corresponding tank bottom cavity is realized, and the mechanical efficiency of the pump is improved.

According to the working pressure of the hydraulic vane pump, the working load of the spring can be converted into different blade bottom pressure areas, and the radial area of the pin or/and the working load of the spring are/is used for configuring the effective pressure area of the blade bottom.

In the whole action period, in the working condition that working cavities at the front side and the rear side of each blade contain working fluid with different pressures and high-pressure working fluid at the same time, the sum of the radial area of a hydraulic action part at the bottom of each blade corresponding to the same blade and the effective pressure-bearing area converted by the working load of a spring is used as the effective pressure-bearing area at the bottom of each blade; in the working condition that working cavities on the front side and the rear side of the blade simultaneously contain low-pressure working fluid, the sum of the radial area of a pin corresponding to the blade and the effective compression area of the work load conversion of a spring is used as the effective compression area of the bottom of the blade; therefore, the contact stress formed by the blade head and the inner surface of the stator in different sections through hydraulic force is properly adjusted, and the working pressure of the pump is improved.

Example 7, see fig. 1, 2, 3, 4, 5, 6, 9, 10, 11, 12, 74-86, this example is a dual acting hydraulic vane pump.

The difference between this embodiment and embodiment 6 is that in this embodiment, in order to ensure the strength of the vane, the vane portion front side balancing chamber four 048-1 included in the front side balancing chamber four 048 and the vane portion rear side balancing chamber four 047-1 included in the rear side balancing chamber four 047 of embodiment 6 are removed.

The rest corresponds to the description in example 6.

Embodiment 8, see fig. 1, 2, 3, 4, 5, 6, 9, 10, 11, 12, 74-86, is a dual acting hydraulic vane pump.

The difference between this embodiment and embodiment 6 is that for the sake of processing convenience, in this embodiment, the rotor portion front side balance chamber four 048-2 included in the front side balance chamber four 048 and the rotor portion rear side balance chamber four 047-2 included in the rear side balance chamber four 047 in embodiment 6 are omitted.

The rest corresponds to the description in example 6.

Embodiment 9, referring to fig. 1, 2, 3, 4, 5, 6, 9, 10, 11, 12, 74 to 86, this embodiment is a double acting hydraulic vane pump.

The difference between this embodiment and embodiment 6 is that when the working chambers on the front and rear sides of the vane are in operation to communicate with the extended suction port, the radial area of the pin can ensure that the vane is kept in contact with the inner surface of the stator, and for the sake of convenience of processing, the spring hole provided in the rotor and the spring placed in the spring hole are eliminated. The working load of the spring is not described in this embodiment.

The rest corresponds to the description in example 6.

Embodiment 10, see fig. 1, 2, 3, 4, 5, 6, 9, 10, 11, 12, 74-86, is a double acting hydraulic vane pump.

The difference between this embodiment and embodiment 6 is that the working load of the spring during the operation of communicating the front and rear working chambers of the vane with the extended suction port ensures that the vane is kept in contact with the inner surface of the stator, and the pin hole provided in the rotor and the pin placed in the pin hole are eliminated for the convenience of processing. No description is made of the radial area of the pin in this embodiment.

The rest corresponds to those described in example 6.

Embodiment 11, see fig. 1, 2, 9, 10, 28 to 33, 74 to 81, and 87 to 89, is a single-acting hydraulic vane pump, which mainly includes: the left pump casing 1, the stator 2, the rotor 3, the blades 4, the left end cover 5, the right end cover 5-1, the pin 71, the right pump casing 1-1 and the transmission shaft 10.

fig. 32 and 33 show the stator 2 used in the present embodiment, and the inner surface of the stator is provided with: 1. the section is away from the axle center distance and increases the curved surface of hole enlargement section that becomes more continuously, a section is away from the reducing section curved surface that the axle center distance becomes less continuously, a section connects the curved surface of hole enlargement section and reducing section curved surface and uses R as the curved surface of radius, a section connects reducing section curved surface and the curved surface of hole enlargement section and uses R as the curved surface of radius.

Fig. 28 and 29 show a right end cap 5-1 adopted in the present embodiment, in which: an extended suction inlet I95 with an included angle alpha 4, an extended discharge outlet I96 with an included angle alpha 5, and an auxiliary channel I80 which is communicated with the extended discharge outlet and has an included angle alpha 6, wherein the liquid distribution path, the circumferential position, the radial position and the shape of the auxiliary channel I are consistent with those of the left end cover. (the angles of the included angles of the extended suction port alpha 4, the extended discharge port alpha 5 and the auxiliary channel alpha 3 can be adjusted appropriately according to the experience of the professional engineer)

Referring to fig. 87 and 88, referring to fig. 9 and 10, the rotor 3 adopted in the present embodiment is shown, and the rotor includes an inner bore bushing 3-1, a 1 × 45 ° chamfer is provided between the radial outer surface of the rotor and both end faces of the rotor, 9 vane grooves 39 are provided in the rotor, a pin hole 711 is provided in the axial center of the bottom of each vane groove, a pin 71 is provided in the pin hole, an annular channel 7121 communicating the bottom chambers of the pins is provided in the rotor, three inclined hole channels 7122 capable of obtaining high-pressure working fluid are provided between the annular channel and both end faces of the rotor in the axial direction, the annular channel and the inclined hole channels form a pin bottom chamber fluid distribution channel 712, the radial positions of the inclined hole channels at both ends of the rotor in the axial direction correspond to the radial positions of the auxiliary channels one 80 in the left and right end covers, and at least one of the inclined hole channels communicates with one of the auxiliary channels one of the left and right end covers in operation, so that the bottom chambers of the pins always contain the high-pressure working fluid.

FIG. 89 is a schematic view showing the main liquid distribution route of the tank bottom chamber in this embodiment;

the other structural arrangements of this embodiment are the same as those of embodiment 6, and this embodiment replaces the description of the extended suction inlet 93, the extended discharge outlet 94 and the auxiliary passage 79 in embodiment 6 with the extended suction inlet one 95, the extended discharge outlet one 96 and the auxiliary passage one 80, and the rest is the same as that described in embodiment 6.

Embodiment 12, referring to fig. 1, 2, 3, 4, 5, 6, 9, 10, 11, 12, 65, 66 fig. 90-103, this embodiment is a double acting hydraulic vane pump, which mainly comprises: the left pump casing 1, the stator 2, the rotor 3, the blades 4, the left end cover 5, the right end cover 5-1, the pin 71, the sub-blades 4-1, the right pump casing 1-1 and the transmission shaft 10.

This example uses the stator, left end cap, right end cap and sub-vanes described in example 4.

fig. 90 and 91, referring to fig. 9 and 10, show a rotor 3 adopted in the present embodiment, where the rotor includes an inner bore bushing 3-1, a chamfer of 1 × 45 ° is provided between a radial outer surface of the rotor and two end faces of the rotor, 10 vane slots 39 are provided in the rotor, a pin hole 711 is provided in the bottom of each vane slot axially in the center, a pin 71 is provided in the pin hole, a slot bottom cavity front side balance channel two 34 is provided between a front side working cavity of the vane and a slot bottom cavity where the vane is located, so that the corresponding slot bottom cavity is an extension end of the front side working cavity, an annular channel 7121 communicating with each pin bottom cavity is provided in the rotor, three inclined hole channels 7122 capable of obtaining high-pressure working fluid are provided between the annular channel and two end faces of the rotor axially, and the annular channel and the inclined hole channels constitute a pin bottom cavity fluid distribution channel 712; the radial positions of the two ends of the inclined hole channels in the axial direction of the rotor correspond to the radial positions of the auxiliary channels 79 in the left end cover and the right end cover, and in operation, at least one inclined hole channel is communicated with one of the auxiliary channels in the left end cover and the right end cover, so that the bottom cavity of the pin always contains high-pressure working liquid.

FIGS. 92 to 99 show the embodiment using the vane 4, in which the axial position of the tail of the vane away from the pin hole of the center post of the rotor is symmetrically provided with two grooves 46 with the same radial area, and the vane is arranged in the vane groove of the rotor;

referring to fig. 103, a vane intermediate chamber 489 is formed between the vane grooves, the vane grooves and the upper portion of the sub-vane.

Each working cavity which contacts with the extending suction inlet 93 and contacts with the stator inner surface diameter expansion section guides suction pressure working fluid into the cavity from the outside of the pump when the volume is increased, each working cavity which contacts with the extending discharge outlet 94 and contacts with the stator inner surface diameter expansion section discharges discharge pressure working fluid out of the cavity when the volume is decreased, and the working fluid pressure in each working cavity has the characteristic of section change; the front side balance channel 31 of each slot bottom cavity ensures that the working fluid pressure in the front side working cavity corresponding to each slot bottom cavity determines the working fluid pressure in the corresponding slot bottom cavity;

Referring to fig. 92 and 94, referring to fig. 65 and 66, the tail of the blade is provided with two grooves, and two sub-blades are arranged in the grooves to correspondingly form two middle cavities; fig. 101 and 102 show the main liquid distribution routes of the slot bottom cavity and the vane intermediate cavity, fig. 103 is an enlarged view of a part I of fig. 101, the vane shown in fig. 103 is positioned at the maximum radial position, the vane in the figure is taken as the front vane of the rear working cavity, and two sets of intermediate cavity rear intermittent liquid distribution passages two 0143 are respectively arranged between the two vane intermediate cavities and the rear working cavity in the corresponding positions axially separated by the vane and the rotor; a vane in the figure is used as a rear vane of the front working cavity, and two intermediate cavity front intermittent liquid distribution channels two 0144 are respectively arranged between the two vane intermediate cavities and the front working cavity in corresponding positions axially separated by the vane.

As shown in fig. 103, the second intermediate chamber rear intermittent liquid distribution passage 0143 is provided:

the virtual boundary lines after the intersected boundary lines 003 of the rear side surfaces of the blade grooves and the radial outer surfaces of the rotors are radially displaced by about 4/15H are respectively used as the radial starting boundaries of two rotor part channels 01431 of two middle cavity rear intermittent liquid distribution channels, the virtual boundary lines after the intersected boundary lines 003 of the radial inner diameter are radially displaced by about 22/15H are respectively used as the radial ending boundaries of the two rotor part channels, the two middle cavity rear intermittent liquid distribution channel two rotor part channels 01431 are opened in a slotted mode, and the intersected boundary lines 003 of the rear side surfaces of the blade grooves and the radial outer surfaces of the rotors are respectively used as the radial starting boundaries of two middle cavity rear intermittent liquid distribution channel two blade part channels 01432 to open the blade heads in a slotted mode;

the rotor part channel 01431 and the blade part channel 01432 correspond in radial position and can be intermittently matched and communicated in work to form two groups of intermediate cavity rear side intermittent liquid distribution channels two 0143, and the intermediate cavity rear side intermittent liquid distribution channels two 0143 regulate and control the connection and disconnection of the rear side working cavity and the corresponding blade intermediate cavity by utilizing the radial telescopic displacement of the corresponding blades.

As shown in fig. 103, the second intermediate chamber front intermittent liquid distribution passage 0144 is provided:

and a boundary line 004 formed by intersecting the outer diameter surface of the rotor and the blades and shifting towards the outer diameter by about 11/15H is respectively used as a radial starting boundary of a front intermittent liquid distribution channel II 0144 of the two intermediate cavities, the blade intermediate cavities are respectively opened towards the inner diameter direction in a slotted mode, and the front intermittent liquid distribution channel II 0144 of the intermediate cavity regulates and controls the connection and disconnection of the front working cavity and the corresponding blade intermediate cavity by utilizing the radial telescopic displacement of the corresponding blade. (the opening depth, the cross-sectional area and the radial position of the second intermediate cavity front side intermittent liquid distribution channel and the second intermediate cavity rear side intermittent liquid distribution channel can be properly adjusted according to the experience of professional engineers)

Referring to fig. 102 and 103, in this embodiment, the pressure of the front side of the vane contacting the high-pressure working fluid corresponds to the working condition that the rear side of the vane receives the low-pressure working fluid, the pressure of the front side of the vane contacting the high-pressure working fluid corresponds to the rear side pressing force of the vane slot, and the pressure of the rear side of the vane contacting the high-pressure working fluid and the fluid flow film corresponds to the working condition that the rear side of the vane contacting the high-pressure working fluid and the front side of the vane slot receives the low-pressure working fluid, the front side pressing force of the vane slot.

91, 94, 95, 97, 98, 99, 103, in response to the operating conditions described for the back side pressing force of the blade groove, back side balance chambers penta 049 are provided on the back side surface of the blade and the back side surface of the blade groove in the corresponding fitting surfaces, respectively, the rotor portion back side balance chamber penta 049-2 having a radially upper end boundary smaller than the maximum radial boundary of the corresponding fitting surface by about 4/15H, axially both end boundaries smaller than the axially both end boundaries of the corresponding fitting surface by about 1/3H, respectively, and a radially lower end boundary larger than the minimum radial boundaries of the corresponding fitting surfaces by about 1 and 4/15H, respectively; the five 049-1 sections of the balancing chambers on the rear side of the blade part, which are separated by the two blade grooves, are radially upper end boundaries which are all larger than the minimum radial boundary of the corresponding matching surface by about 1H, the axial two-end boundaries of the blade part are respectively smaller than the axial two-end boundaries of the corresponding matching surface by about 1/3H, the radial lower end boundaries of the blade part are respectively larger than the minimum radial boundary of the corresponding matching surface by about 3/5H and respectively extend to 3 and 2/15H, and the rest part opens the tail part of the blade; a rotor part rear side balance chamber five 049-2 and a blade part rear side balance chamber five 049-1 form a rear side balance chamber five 049; correspondingly forming the working condition of the front side pressing force of the blade groove; a front balancing chamber five 0410 is provided on the front side of the rotor blade slot in the corresponding mating face, whose radially upper end boundary is less than the maximum radial boundary of the corresponding mating face by about 4/15H, whose axially both end boundaries are less than the axially both end boundaries of the corresponding mating face by about 1/3H, respectively, and whose radially lower end boundary is greater than the minimum radial boundary of the corresponding mating face by about 9/10H.

The area of the rear balance chamber five 049 comprises the area of the intermediate cavity rear intermittent liquid distribution channel second rotor part channel 01431, the area of the front balance chamber five 0410 comprises the area of the intermediate cavity front intermittent liquid distribution channel second 0144, under any working condition, the front balance chamber five and the rear balance chamber five are communicated with each other through the blade intermediate cavity and the groove bottom cavity or are communicated with each other through the blade intermediate cavity, and the rear balance chamber five is combined with the front balance chamber five to adjust the rear pressing force of the blade groove and the front pressing force of the blade groove.

Corresponding to a rear matching surface reserved in the rear balancing chamber five 049, rear liquid distribution channels five 0409 are respectively arranged between the rear side surfaces of two lower end part blades axially separated in the rear side surface of the blade in the reserved rear matching surface and a rear working cavity of the blade, the maximum radial boundary of the rear liquid distribution channels in the arrangement is leveled with the intersecting boundary line of the rear side surface of the blade groove and the radial outer surface of the rotor, the rear liquid distribution channels five enable the rear side plane of the blade positioned at the maximum radial position to be contacted with low-pressure working liquid through chamfers at the two axial ends of the radial outer surface of the rotor, correspondingly form the working condition of rear blade groove rear pressure regulation, and reasonably correct the radial distribution of the rear pressure of the regulated blade groove, so that a fitting trend is established between the rear side surface of the blade in the residual part of the rear balancing chamber five in the corresponding matching surface and the rear side surface of the blade groove; (see in detail fig. 91, 94, 95, 96, 97, 99, 100), taking the boundary line 003 of the intersection of the rear side surface of the vane slot and the radially outer surface of the rotor as the support line of the rear side pressing force of the vane slot (see fig. 103), in this embodiment, the moment of the pressing force acting on the radially inner end of the support line is greater than the moment of the outer end of the support line, so that the remaining part of the rear side balance chamber five 049 in the corresponding mating surface is used as a rear side low pressure mating surface, thereby the vane in the working condition is subjected to working displacement in the corresponding mating, and the rear side balance chamber five 049 is isolated from the rear working chamber at the maximum radially outer end and the axial both ends of the mating surface (see in detail 242 nodes of fig. 101); the trailing side dosing channel does not allow the portion of the trailing side of the vane in displacement to communicate with the trailing side working chamber (see in detail 244 of fig. 102) until the vane is retracted to the minimum radial position.

In the embodiment, the moment of the radial inner end of the supporting line applied by the pressing force is greater than the moment of the radial outer end of the supporting line, so that the remaining part of the front balancing chamber five 0410 in the corresponding matching surface is used for contacting the front attachment surface of the high-pressure working fluid, thereby causing the blade in the working condition to perform working displacement in the corresponding attachment, and isolating the front balancing chamber five 0410 from the front working cavity. (see node 244 in FIG. 102) (the opening depth of the balance chamber is about 2/15H, and the opening depth of the balance chamber, the area of the balance chamber and the abutting surface can be adjusted according to the experience of professional engineers)

As shown by point 242 in fig. 101, in the operation of the blade corresponding to the rear-side pressing force of the blade groove, the extending discharge port, the second intermediate chamber front intermittent fluid distribution passage 0144, the second front groove bottom chamber common fluid distribution passage 34, the auxiliary passage and the pin bottom chamber fluid distribution passage are respectively provided to contact the blade head front portion, the blade intermediate chamber, the remaining blade tail portion and the pin tail portion corresponding to the same blade with the high-pressure fluid, and the extending suction port is provided to contact the blade head rear portion with the low-pressure fluid; as shown by 244 in fig. 102, in the operation of the vane corresponding to the pressing force on the front side of the vane groove, the discharge port, the second 0143 of the intermittent fluid distribution channel on the rear side of the intermediate chamber, the auxiliary channel and the fluid distribution channel on the bottom chamber of the pin are extended, the rear part of the head of the vane, the intermediate chamber of the vane and the tail of the pin corresponding to the vane are respectively contacted with the high-pressure working fluid, the second 34 of the balancing channel on the front side of the suction port and the bottom chamber of the groove is extended, the remaining tail part of the vane and the front part of the head of the vane are respectively contacted with the low-pressure working fluid, and the total radial area of the intermediate chamber of the vane and the pin corresponding to the vane is designed, part of the hydraulic force generated by the total radial area is used for balancing the hydraulic force generated by the rear part of the head of the vane, and the remaining liquid force is used for overcoming the pressing force on the front side of the vane groove and keeping the vane extending towards the outer diameter. The total radial area of the vane middle cavity and the pin connected with the same vane in the working condition is the effective pressure bearing area of the bottom of the vane. (the radial area of the front part of the blade head, the radial area of the pin and the area of the blade intermediate chamber can be adjusted according to the experience of the professional engineer under the requirement of ensuring that the blade maintains proper contact stress with the inner surface of the stator during the whole operation)

Referring to fig. 101 and 102, the main ways of obtaining the liquid distribution of the corresponding tank bottom cavity 89, pin bottom cavity and vane middle cavity when the vane head contacts different circumferential nodes with the inner surface of the stator are shown, and correspondingly, the comparison between the hydraulic force for expanding the vane outward radial direction obtained by the pin tail, the vane middle cavity and the remaining vane tail and the total hydraulic force for retracting the vane inward radial direction obtained by each part of the vane head is shown:

in operation, as shown in point 241 in fig. 101, the front and rear working chambers of the blade are simultaneously communicated with the extension suction inlet, the corresponding bottom chamber of the blade is communicated with the front working chamber through the front balancing channel II 34 of the bottom chamber of the blade, the middle chamber of the blade is communicated with the front working chamber through the front intermittent liquid distribution channel II 0144 of the middle chamber and is communicated with the rear working chamber through the rear intermittent liquid distribution channel II 0143 of the middle chamber, and the bottom chamber of the pin is communicated with the extension discharge outlet through the auxiliary channel and the liquid distribution channel of the bottom chamber of the pin; the front part of the head of the blade, the rear part of the head of the blade, the tail of the residual blade and the middle cavity of the blade corresponding to the blade are all contacted with low-pressure working fluid P1, the tail of the pin is contacted with high-pressure working fluid P2, and the pin pushes the blade to keep the outward diameter expansion trend by proper hydraulic force generated by the high-pressure working fluid at the tail of the pin;

at point 242 in fig. 101, the front working chamber of the vane communicates with the extended exhaust port, the rear working chamber remains to communicate with the extended intake port, the corresponding bottom chamber of the vane communicates with the front working chamber through the second front balancing channel 34 of the bottom chamber of the vane, the middle chamber of the vane communicates with the front working chamber through the second front intermittent liquid distribution channel 0144 of the middle chamber, and the bottom chamber of the pin communicates with the extended exhaust port through the auxiliary channel and the liquid distribution channel of the bottom chamber of the pin; the front part of the blade head, the tail part of the residual blade, the tail part of the pin and the middle cavity of the blade corresponding to the blade are all contacted with high-pressure working fluid P2, the rear part of the blade head corresponding to the blade is contacted with low-pressure working fluid P1, and the blade keeps the stretching trend towards the outer diameter by proper hydraulic force generated by the high-pressure working fluid contacted with the tail part of the pin, the middle cavity of the blade and the tail part of the residual blade;

at point 243 in fig. 102, the front and rear working cavities of the vane are simultaneously communicated with the extended discharge port, the corresponding groove bottom cavity is communicated with the rear working cavity through the groove bottom cavity front side balance channel two 34, the vane middle cavity is communicated with the front working cavity through the middle cavity front side intermittent liquid distribution channel two 0144 and is communicated with the rear working cavity through the middle cavity rear side intermittent liquid distribution channel two 0143, and the pin bottom cavity is communicated with the extended discharge port through the auxiliary channel and the pin bottom cavity liquid distribution channel; the front part of the blade head, the rear part of the blade head, the tail of the residual blade, the tail of the pin and the middle cavity of the blade which correspond to the blade are all contacted with high-pressure working fluid P2, and the radial position of the blade is limited by the reducing section of the inner surface of the stator;

at 244 in fig. 102, the blade rear working chamber is communicated with the extended discharge port, the front working chamber is communicated with the extended suction port, the corresponding tank bottom chamber is communicated with the front working chamber through the tank bottom chamber front balancing channel two 34, the blade middle chamber is communicated with the rear working chamber through the middle chamber rear intermittent liquid distribution channel two 0143, and the pin bottom chamber is communicated with the extended discharge port through the auxiliary channel and the pin bottom chamber liquid distribution channel; the front part of the head of the blade and the tail of the residual blade are contacted with low-pressure working fluid P1, the middle cavity of the blade, the tail of the pin and the rear part of the head of the blade corresponding to the blade are contacted with high-pressure working fluid P2, the sum of the radial area of the pin and the radial area of the middle cavity of the blade is larger than the radial area of the rear part of the head of the blade, and the blade keeps the outward diameter expansion trend by proper hydraulic force generated by the high-pressure working fluid contacted with the tail of the pin and the middle cavity of the blade;

when the blade works to the point 241, the next working cycle is started.

in the whole action period, the intermittent liquid distribution channel II on the front side of the middle cavity is combined with the intermittent liquid distribution channel II on the rear side of the middle cavity, so that the corresponding blade middle cavity can lead suction pressure working liquid into the cavity through the corresponding working cavity in volume expansion, and the corresponding blade middle cavity can discharge pressure working liquid in the cavity to the outside of the pump through the corresponding working cavity in volume reduction, so that the flow of the working liquid generated in the volume change process of the blade middle cavity in work is totally summarized into the calculated discharge capacity of the pump, the volume efficiency of the hydraulic vane pump in the embodiment is improved, and the working pressure is also improved; the working fluid pressure in the corresponding blade middle cavity is determined by the circumferential position of the rear side working cavity and/or the front side working cavity communicated with the rear side working cavity and/or the front side working cavity on the inner surface of the stator, so that optimized liquid distribution of segmental adjustment pressure obtained by the corresponding blade middle cavity is realized, and the mechanical efficiency of the pump is improved.

The rest corresponds to the description in example 4.

The above embodiments have been described with a double acting hydraulic vane pump instead of a multiple acting hydraulic vane pump; the above examples are intended to illustrate the invention, but not to limit it.

Claims

1. A rotor blade assembly, comprising: the blade is arranged in the inner cavity of the stator of the hydraulic vane pump, is provided with a rotor which is distributed with a plurality of blade grooves along the circumference and can rotate, and the head part of the blade is provided with a contact angle or two contact angles and can be arranged in the blade grooves in a telescopic motion way;

corresponding to the working rotation direction of the rotor: rear side matching surfaces which can be mutually contacted exist between part of the rear side surfaces of the blades and the corresponding rear side surfaces of the blade grooves, and front side matching surfaces which can be mutually contacted exist between part of the front side surfaces of the blades and the corresponding front side surfaces of the blade grooves; the contact part of the blade of one contact angle and the inner surface of the stator divides the blade head into a front part of the blade head and a back part of the blade head; the blade head is divided into a blade head front side part, a blade head middle part and a blade head rear side part by two contact positions of the blades with the two contact angles and the inner surface of the stator;

the blade adopts a contact angle: a rear-side balancing channel of the bottom cavity is arranged in the corresponding part of the rotor between the rear-side working cavity communicated with the rear part of the head part of the blade and the bottom cavity of the rotor where the blade is positioned, or a front-side balancing channel of the bottom cavity is arranged in the corresponding part of the rotor between the front-side working cavity communicated with the front part of the head part of the blade and the bottom cavity where the blade is positioned; the blade adopts two contact angles: a middle balancing channel of the bottom cavity of the groove is arranged between the middle part of the head of the blade and the bottom cavity of the groove where the blade is positioned in the corresponding part of the blade;

the method is characterized in that:

a rear side balancing chamber is arranged on the rear side surface of the blade or/and the rear side surface of the blade groove in the range of part of the rear side matching surface corresponding to the rear side matching surface of the blade at the maximum radial position;

a front side matching surface corresponding to the vane at the minimum radial position, wherein a front side balance chamber is arranged on the front side surface of the vane or/and the front side surface of the vane slot within the range of part of the front side matching surface;

the rear side balance chamber and the front side balance chamber corresponding to the same blade are communicated all the time, in the work process, the working fluid pressure in the rear side balance chamber corresponding to the blade located at the maximum position is determined by the working fluid pressure in the front side balance chamber corresponding to the blade located at the minimum position, and the working fluid pressure in the front side balance chamber corresponding to the blade located at the minimum position is determined by the working fluid pressure in the rear side balance chamber corresponding to the blade located at the minimum position.

2. The rotor blade assembly of claim 1, wherein: a rear side liquid distribution passage for communicating the former with the latter is provided in the corresponding part of the vane or the vane and the rotor, and the rear side liquid distribution passage is terminated to communicate the former with the latter in the displacement before the vane retracts to the minimum radial position in the operation; the blade is provided with a middle balancing channel with a groove bottom cavity, a rear side matching surface reserved corresponding to the rear side balancing chamber in the setting, a part of the rear side surface of the blade in the reserved rear side matching surface is taken as the former, a rear side working cavity of the blade is taken as the latter, and a rear side liquid distribution channel enabling the former to be communicated with the latter is arranged in the corresponding part of the blade or the blade and the rotor.

3. A hydraulic vane pump, comprising: the device comprises a pump shell with a fluid inlet and a fluid outlet, a stator which is arranged in the pump shell and provided with one or more groups of diameter expanding sections and diameter reducing sections corresponding to the rotation direction of a rotor on the surface of an inner cavity, a left end cover and a right end cover which are arranged at the two axial ends of the stator, a rotor which is provided with a plurality of blade grooves distributed along the circumference and blades arranged in the blade grooves and a transmission shaft which is arranged at one side of the pump shell in a penetrating way and is linked with the rotor;

the left end cover and the right end cover: the pump shell is provided with a suction inlet and a working cavity, the suction inlet is arranged between the suction inlet and the working cavity is in contact with the diameter-expanded section of the inner surface of the stator, the discharge outlet is arranged between the discharge outlet and the working cavity is in contact with the diameter-reduced section of the inner surface of the stator, the discharge outlet is provided with an auxiliary channel, one end of the auxiliary channel is communicated with the discharge outlet, and the circumferential positions of the extension suction inlet, the extension discharge outlet and the auxiliary channel in the left end cover and the right end cover respectively correspond to each other; the extension suction inlet and the extension discharge outlet are arranged at intervals along the circumferential direction and cannot be communicated with the same working cavity at the same time; in the working process, the working cavity contacting with the diameter expanding section guides suction pressure working fluid into the cavity from the outside of the pump when the volume is increased, and the working cavity contacting with the diameter reducing section discharges discharge pressure working fluid to the outside of the cavity when the volume is reduced;

the method is characterized in that: the hydraulic vane pump employs a rotor vane assembly as claimed in claims 1 to 2 for the rotor and vanes housed in the stator cavity.

4. The hydraulic vane pump of claim 3, wherein: the pin and/or the spring are/is additionally arranged in the rotor blade assembly; the added pin is as follows: the bottom of the blade groove of the rotor with the inner hole bushing is provided with a pin hole, and a pin is arranged in the pin hole; a pin bottom cavity is formed between the tail of the pin and the bottom of the pin hole; an annular channel communicated with each pin bottom cavity is arranged in the rotor, a plurality of inclined hole channels are arranged between the annular channel and two axial end faces of the rotor, and the annular channel and the inclined hole channels form a pin bottom cavity liquid distribution channel; the radial positions of the inclined hole channels of the liquid distribution channel of the bottom cavity of the pin correspond to the auxiliary channels in the left end cover and the right end cover respectively in the axial direction of the rotor, and at least one inclined hole channel in the liquid distribution channel of the bottom cavity of the pin is communicated with the auxiliary channels in the left end cover and the right end cover, so that the tail part of the pin is always in contact with and discharges pressure working liquid in the whole working process; the additional spring is as follows: spring holes are arranged between the blades and the rotor and on corresponding parts, and springs are arranged in the spring holes; the axial position of the pin or/and the spring is determined by the bottom axial balanced stress requirement of the corresponding blade in the working process; the vane is in contact with the inner surface of the stator, and the radial area of the pin contacting with the pressure working fluid to be discharged or/and the working load of the spring are designed correspondingly.

5. The hydraulic vane pump of claim 4 wherein: the rotor blade assembly adopts a contact angle blade, another pin is additionally arranged in the rotor blade assembly, another pin hole is arranged at the bottom of the blade groove and axially departs from the pin hole, and another pin is arranged in the other pin hole; the axial position of the other pin is determined by the bottom axial balanced stress requirement of the corresponding blade in the working process; another pin bottom cavity is formed between the tail end of the other pin and the bottom of the other pin hole, and the other pin bottom cavity where the other pin is located is the other pin bottom cavity corresponding to the other pin connecting blade; a rear side intermittent liquid distribution channel of another pin bottom cavity is arranged between the rear side working cavity of the blade and the other pin bottom cavity corresponding to the blade in the corresponding part of the rotor blade assembly, and the rear side intermittent liquid distribution channel of the other pin bottom cavity is used for enabling the rear side working cavity of the blade to be communicated with the other pin bottom cavity corresponding to the blade when the corresponding blade is positioned at the minimum and smaller radial positions; another pin bottom cavity front side intermittent liquid distribution channel is arranged in a corresponding part of the rotor blade assembly between the front side working cavity of the blade and the other pin bottom cavity corresponding to the blade, and the other pin bottom cavity front side intermittent liquid distribution channel is used for enabling the blade front side working cavity to be communicated with the other pin bottom cavity corresponding to the blade when the corresponding blade is positioned at the maximum and larger radial positions; during operation, the other pin bottom cavity corresponding to the blade is communicated with the rear side working cavity of the blade through the other pin bottom cavity rear side intermittent liquid distribution channel or/and is communicated with the front side working cavity of the blade through the other pin bottom cavity front side intermittent liquid distribution channel.

6. The hydraulic vane pump of claim 5 wherein: the rotor blade assembly;

adopt groove bottom chamber rear side balanced passageway: the front part of the blade head, which is communicated with the extended suction inlet, is designed correspondingly to keep the blade in contact with the inner surface of the stator in the process of utilizing the pressure difference of the working fluid, so that the front part of the blade head, which is communicated with the extended suction inlet, is designed correspondingly to be in contact with the blade in the process of utilizing the pressure difference of the working fluid; the other pin radial area which is connected with the blade and is communicated with the extension outlet is correspondingly designed and additionally arranged when the blade is required to be kept in contact with the inner surface of the stator in the process of utilizing the pressure difference of the working fluid;

adopt groove bottom chamber front side balanced passageway: the radial area of the back part of the blade head communicated with the extended suction inlet is correspondingly designed when the blade is kept in contact with the inner surface of the stator in the process of utilizing the working fluid pressure difference; the corresponding back side working cavity is communicated with the extended discharge port, the front side working cavity is communicated with the extended suction port and contacts with the blade in working of working fluid with different pressure, and in order to enable the blade to keep contact with the inner surface of the stator in the process of utilizing the pressure difference of the working fluid, another pin radial area which is connected with the blade and is communicated with the extended discharge port is correspondingly designed.

7. The hydraulic vane pump of claim 4 wherein: the rotor blade assembly adopts a contact angle blade, a blade middle cavity is additionally arranged in the rotor blade assembly, a groove is formed in the lower part of the blade and axially departs from the pin, and a sub-blade is arranged in the groove; the blade middle cavity corresponding to the blade is correspondingly formed among the lower part of the blade, the sub-blade and the blade groove; the axial position of the blade middle cavity is determined by the bottom axial balanced stress requirement of the corresponding blade in the working process; an intermediate cavity rear side intermittent liquid distribution channel is arranged between the rear side working cavity of the blade and the blade intermediate cavity corresponding to the blade in the corresponding part of the rotor blade assembly, and the intermediate cavity rear side intermittent liquid distribution channel is used for enabling the blade rear side working cavity to be communicated with the blade intermediate cavity corresponding to the blade when the corresponding blade is positioned at the minimum radial position and the smaller radial position; an intermediate cavity front side intermittent liquid distribution channel is arranged between the front side working cavity of the blade and the blade intermediate cavity corresponding to the blade in the corresponding part of the rotor blade assembly, and the intermediate cavity front side intermittent liquid distribution channel is used for enabling the blade front side working cavity to be communicated with the blade intermediate cavity corresponding to the blade when the corresponding blade is positioned at the maximum radial position and the larger radial position; during working, the blade middle cavity corresponding to the blade is communicated with the rear side working cavity of the blade through the middle cavity rear side intermittent liquid distribution channel or/and communicated with the front side working cavity of the blade through the middle cavity front side intermittent liquid distribution channel.

8. The hydraulic vane pump of claim 7 wherein: the rotor blade assembly;

adopt groove bottom chamber rear side balanced passageway: the radial area of the front part of the blade head, which is communicated with the extension suction inlet, is correspondingly designed when the blade is kept in contact with the inner surface of the stator in the process of utilizing the working fluid pressure difference; the radial area of the middle cavity of the blade, which corresponds to the blade and is communicated with the extension outlet, is correspondingly designed to be increased when the blade is in contact with the inner surface of the stator in the process of utilizing the pressure difference of the working fluid;

adopt groove bottom chamber front side balanced passageway: the radial area of the back part of the blade head, which is communicated with the extension suction inlet, is correspondingly designed when the blade is kept in contact with the inner surface of the stator in the process of utilizing the working fluid pressure difference; the blade is contacted with the blade in working of working fluid with different pressure by the corresponding rear working cavity communicated with the extended discharge port and the front working cavity communicated with the extended suction port, and the radial area of the middle cavity of the blade, which is corresponding to the blade and communicated with the extended discharge port, is additionally designed correspondingly to ensure that the blade is kept in contact with the inner surface of the stator in the process of utilizing the pressure difference of the working fluid.

9. The hydraulic vane pump of claim 4 wherein: the rotor blade assembly adopts two contact angle blades, a groove bottom cavity rear side intermittent liquid distribution channel is arranged between a rear side working cavity of each blade and a groove bottom cavity of the corresponding part of the rotor blade assembly in the corresponding position of the corresponding part of the rotor blade assembly, and the groove bottom cavity rear side intermittent liquid distribution channel is used for enabling the corresponding blade to be positioned on the minimum radial position and the smaller radial position, and the blade rear side working cavity is communicated with the groove bottom cavity of the corresponding blade; a groove bottom cavity front side intermittent liquid distribution channel is arranged between the front side working cavity of the blade and the groove bottom cavity of the blade in the corresponding part of the rotor blade component, and the groove bottom cavity front side intermittent liquid distribution channel is used for enabling the blade front side working cavity to be communicated with the groove bottom cavity of the blade in the maximum radial position and the larger radial position of the corresponding blade; when the middle part of the blade head contacts the diameter expanding section and the front contact angle of the blade head is separated from the inner surface of the stator, a front side clearance channel is generated between the middle part of the blade head and the front side working cavity, or when the middle part of the blade head contacts the diameter reducing section and the rear contact angle of the blade head is separated from the inner surface of the stator, a rear side clearance channel is generated between the middle part of the blade head and the rear side working cavity; in operation, the middle balance channel of the bottom cavity of the blade is matched with the front clearance channel or the rear clearance channel, and the bottom cavity of the blade is at least communicated with the adjacent working cavity of the blade by combining the rear intermittent liquid distribution channel of the bottom cavity of the blade and the front intermittent liquid distribution channel of the bottom cavity of the blade.

10. The hydraulic vane pump of claim 9, wherein: the rotor blade assembly;

the middle balance channel of the groove bottom cavity is adopted: the radial area of the front part of the blade head, which is communicated with the extension suction inlet, is correspondingly designed when the blade is kept in contact with the inner surface of the stator in the process of utilizing the working fluid pressure difference; the radial area of the back part of the blade head communicated with the extended suction inlet is correspondingly designed to ensure that the blade is kept in contact with the inner surface of the stator in the process of utilizing the working fluid pressure difference.