CN117006010A - Floating swash plate type axial plunger pump based on return disc rotation driving - Google Patents
Floating swash plate type axial plunger pump based on return disc rotation driving Download PDFInfo
- Publication number
- CN117006010A CN117006010A CN202310479210.2A CN202310479210A CN117006010A CN 117006010 A CN117006010 A CN 117006010A CN 202310479210 A CN202310479210 A CN 202310479210A CN 117006010 A CN117006010 A CN 117006010A
- Authority
- CN
- China
- Prior art keywords
- oil
- disc
- cylinder body
- rotary disc
- swash plate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000007667 floating Methods 0.000 title claims abstract description 23
- 230000003068 static effect Effects 0.000 claims abstract description 29
- 230000002706 hydrostatic effect Effects 0.000 claims description 15
- 238000013016 damping Methods 0.000 claims description 8
- 230000000149 penetrating effect Effects 0.000 claims description 7
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims 1
- 238000005461 lubrication Methods 0.000 abstract description 7
- 230000009286 beneficial effect Effects 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 92
- 230000033001 locomotion Effects 0.000 description 8
- 238000005299 abrasion Methods 0.000 description 4
- 230000001154 acute effect Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 3
- 239000004519 grease Substances 0.000 description 3
- 239000010720 hydraulic oil Substances 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 239000000306 component Substances 0.000 description 2
- 239000008358 core component Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 239000011148 porous material Substances 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 230000009347 mechanical transmission Effects 0.000 description 1
- 238000005245 sintering Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
The invention discloses a floating inclined disc type axial plunger pump based on return disc rotation driving, which comprises a pump body, wherein a valve plate, a cylinder body, a return disc, a rotary disc and an inclined disc which are connected in series by a main shaft are arranged in the pump body, the cylinder body, the return disc and the rotary disc synchronously rotate along with the main shaft, one end of a plurality of sliding shoes in the return disc are used for hinging a ball head at the end part of a plunger in the cylinder body, the other end of each sliding shoe is contacted with the rotary disc, and static pressure supports are respectively formed between the sliding shoes and the rotary disc, between the rotary disc and the inclined disc and between the cylinder body and the valve plate. According to the invention, the sliding shoes drive the return disc to rotate, and the return disc drives the rotary disc to synchronously rotate based on the connecting pins, so that the sliding shoes do not relatively slide relative to the rotary disc, the friction power loss of the sliding shoe pair is eliminated, the overturning eccentric wear risk of the sliding shoes caused by high-speed centrifugal force is reduced, the rotary disc replaces the distributed sliding shoe pair to be beneficial to realizing high speed of the pump, meanwhile, the flow distribution pair is provided with a static pressure supporting structure, the friction lubrication performance under low-speed working conditions is improved, and the friction wear during low speed is reduced.
Description
Technical Field
The invention relates to the field of plunger pumps, in particular to a floating swash plate type axial plunger pump based on return rotation driving.
Background
Compared with the traditional mechanical transmission, the hydraulic transmission has the advantages of high power density, convenient control, excellent dynamic performance and the like, has wide application in modern industrial systems, especially engineering machinery, and most of engineering machinery in China adopts the hydraulic transmission technology so far. The axial plunger pump is used as one of core components of the hydraulic system, is one of core components of the whole hydraulic system, is a power source component of the whole hydraulic system, has the advantages of high transmission power, long service life, simple and convenient control variable, small volume and the like, and most of engineering machinery hydraulic systems in China use the plunger pump as a power source of the whole hydraulic system. Therefore, the analysis and research on the characteristics of the axial plunger pump plays an important role in improving the performance of the whole hydraulic system.
In recent years, with the continuous development of the mechanical industry in China, more strict requirements are also put on the performance of the plunger pump in various industries. The requirements for high pressure, high speed and high performance of a hydraulic system are increasingly urgent, and the problem of wear resistance and life prolonging of an axial plunger pump is very urgent. The plunger pair and the slipper pair are used as important friction pairs of the swash plate type plunger pump, and friction forces generated by the two large friction pairs are important components of power loss of the swash plate type plunger pump. On the one hand, the friction pair elements slide relatively, if the lubrication condition is poor, the clearance is too small, even long-term solid contact is carried out, heat accumulation is easy to generate, the abrasion is accelerated to reduce the service life, the mechanical loss is increased, and the direct sintering is damaged if the friction pair elements are heavy; on the other hand, too large a gap formed between the friction elements reduces the sealing action of the friction pair, and the leakage amount rapidly increases, thereby reducing the volumetric efficiency of the whole pump.
Along with the development of engineering machinery dynamoelectric, the axial plunger pump is required to reach higher and higher working rotating speed, when the axial plunger pump rotates at high speed, the existing axial plunger pump sliding shoe structure is easy to generate a tilting eccentric wear phenomenon under the action of centrifugal force generated during high-speed rotation, is a typical failure mode of the axial plunger pump, and meanwhile, the existing axial plunger pump sliding shoe structure is a distributed structure, generally, 9 sliding shoes are contained in one pump, the contact area of the sliding shoes and an inclined disc surface is reduced by the distributed sliding shoes, the contact stress and the PV value of a sliding shoe pair are increased, and the realization of high speed of the pump is not facilitated. The 9 shoes which are easy to topple and bias and wear simultaneously do relative sliding and rotating movements at high speed relative to the inclined disc surface, so that the friction power loss and leakage loss of the shoe pair are increased, the fault point is increased, and once one shoe fails, the whole pump can be damaged.
The engineering machinery is electrically transformed, meanwhile, the friction lubrication performance of the internal friction pair of the axial plunger pump under the low-speed working condition is required to be improved, and the existing axial plunger pump flow distribution pair is generally not provided with a static pressure supporting structure, so that a lubrication oil film of the flow distribution pair is formed insufficiently under the low-speed working condition, friction is severe, friction power loss is large, and abrasion failure is easy to occur.
Disclosure of Invention
The invention provides a floating swash plate type axial plunger pump based on return rotation driving, which solves the problems caused by a distributed sliding shoe structure in the swash plate type axial plunger pump and improves the friction lubrication performance of a flow distribution pair under a low-speed working condition through a static pressure supporting structure.
In order to achieve the above purpose, the technical scheme adopted by the invention is as follows:
the utility model provides a floating swash plate type axial plunger pump based on return disc rotary drive, including pump body (14), be equipped with main shaft (1) in pump body (14), and in proper order straight line distribution's valve plate (12), cylinder body (11), rotary disk (6), sloping cam plate (5), install spherical hinge (8) towards the terminal surface center of one end of rotary disk (6) in cylinder body (11), be equipped with a plurality of cylinder bores (17) in cylinder body (11), slidable mounting has plunger (10) in every cylinder bore (17) respectively, each plunger (10) one end is worn out from cylinder body (11) towards the terminal surface of one end of rotary disk (6) respectively, the terminal surface of one end of cylinder body (11) towards valve plate (12) is equipped with the oil orifice (21) of a plurality of one-to-one intercommunication cylinder bores (17), be equipped with a plurality of valve plates (12) that link up in valve plate (12), the one side of rotary disk (6) towards cylinder body (11) is equipped with return disk (9), there are a plurality of connecting pins (16) in return disk (9), every connecting pin (16) are towards rotary disk (6) respectively;
a plurality of through holes are formed in the return disc (9), sliding shoes (7) are respectively arranged in each through hole in a penetrating mode, ball sockets are respectively arranged at one end, facing the cylinder body (11), of each sliding shoe (7), one end, penetrating out of the cylinder body (11), of each plunger (10) is hinged into the ball socket of each sliding shoe (7) in a one-to-one correspondence mode, and the other end of each sliding shoe (7) is in contact with a corresponding surface of the rotary disc (6);
the return disc (9) is also in contact with the spherical hinge (8) through a central through hole of the main shaft (1), the main shaft (1) sequentially penetrates through the center of the valve plate (12), the center of the cylinder body (11), the center of the spherical hinge (8), the center of the rotary disc (6) and the center of the swash plate (5), and the main shaft (1) is connected with the cylinder body (11) and the spherical hinge (8), so that the cylinder body (11) and the spherical hinge (8) integrally rotate along with the main shaft (1) when the main shaft (1) rotates, the return disc (9) rotates, the sliding shoes (7) and the plungers (10) rotate, the rotary disc (6) is driven to rotate through the connecting pins (16) when the return disc (9) rotates, and the side surfaces of the rotary disc (6) and the swash plate (5) are in clearance fit, namely are not in radial contact;
the plunger piston is characterized in that an oil guide through hole is formed in each plunger piston (10), one end of the oil guide through hole is communicated to a corresponding cylinder hole (17), the other end of the oil guide through hole is communicated to a ball socket in a corresponding sliding shoe (7), a static pressure oil chamber (26) is formed in the end face of one end, in contact with a rotary disc (6), of each sliding shoe (7), each static pressure oil chamber (26) is communicated with the ball socket in the corresponding sliding shoe (7), oil entering the cylinder hole (17) of a cylinder body (11) from a valve plate (12) enters the static pressure oil chamber (26) of the sliding shoe (7) through the oil guide through hole of the plunger piston (10) and the ball socket of the sliding shoe (7), and therefore first static pressure bearings are formed between each sliding shoe (7) and the rotary disc (6) through the oil.
Further, the cylinder body (11) faces towards the end face of one end of the valve plate (12) and is in clearance fit with the valve plate (12), oil storage grooves (25) are respectively arranged at positions, corresponding to the oil through holes (21), of one end face of the cylinder body (11) faces towards the valve plate (12), the oil storage grooves (25) are respectively communicated with the corresponding oil through holes (21) through damping holes (24), part of oil in the oil through holes (21) enters the oil storage grooves (25) through the damping holes (24), and then flows into a clearance between the cylinder body (11) and the valve plate (12) to form second static pressure bearings.
Further, clearance fit is provided between rotary disk (6) and sloping cam plate (5), correspond every skid shoe (7) position in rotary disk (6) and be equipped with oil guide way (18) respectively, oil guide way (18) one end communicates with static pressure grease chamber (26) of corresponding skid shoe (7) respectively, oil guide way (18) other end communicates to clearance between rotary disk (6), sloping cam plate (5) respectively, from this the oil storage grease chamber (19) between rotary disk (6) and sloping cam plate (5) are flowed into through oil guide way (18) in static pressure grease chamber (26), form the third static pressure and support.
Furthermore, one surface of the rotary disc (6) facing the swash plate (5) is provided with oil storage chambers (19) corresponding to the positions of the oil guide holes (18), and the other ends of the oil guide holes (18) are respectively communicated with the corresponding oil storage chambers (19), so that oil flows into a gap between the rotary disc (6) and the swash plate (5) through the oil storage chambers (19) to form a third hydrostatic bearing.
Furthermore, a pressure relief ring groove (20) is also arranged on one surface of the rotary disc (6) facing the swash plate (5).
According to the invention, the oil guide hole (18) is formed in the middle of the oil storage chamber on the assembling surface of the rotary disc (6), hydraulic oil of the hydrostatic oil chamber (26) on the bottom surface of the sliding shoe (7) flows into the space between the rotary disc (6) and the swash plate (5) through the oil guide hole (18), and the complete hydrostatic bearing of the rotary disc (6) is realized. Because the sliding shoes (7) drive the return disc (9) to rotate through the neck parts of the sliding shoes, the return disc (9) drives the floating rotary disc (6) which is completely supported by static pressure to rotate through the connecting pins (16), and therefore, no relative sliding movement exists between the sliding shoes (7) and the rotary disc (6) when the axial plunger pump works, and therefore, the phenomenon of overturning and eccentric wear of the sliding shoes (7) caused by centrifugal force is thoroughly eliminated, and the friction power loss of sliding shoe pairs is eliminated. According to the invention, 9 scattered slipper pairs in the existing axial plunger pump are converted into an integral rotary disc rotary pair between the rotary disc (6) and the swash plate (5), the integral rotary disc rotary pair rotates around the central axis of the rotary disc rotary pair on the inclined disc surface, centrifugal forces in the radial directions are mutually offset, the stability and reliability of the rotation are improved, the contact area between the rotary disc (6) and the swash plate (5) is obviously increased compared with the total contact area of 9 scattered slipper pairs of the existing axial plunger pump, the PV value is obviously reduced, and the pump is beneficial to realizing high speed.
According to the invention, the oil through hole (21) and the oil storage tank (25) are arranged on the flow distribution surface of the cylinder body (11) and the flow distribution plate (12), part of hydraulic oil in the oil through hole (21) enters the oil storage tank (25) through the fixed damping hole (24), and a static pressure bearing is formed under the action of the variable clearance fit between the cylinder body (11) and the flow distribution plate (12), so that the friction and lubrication performance of the flow distribution pair during the low-speed working condition of the axial plunger pump can be improved, and the friction and abrasion during the low-speed working condition of the axial plunger pump can be reduced.
Drawings
FIG. 1 is a schematic view of an assembled half-section of a floating swash plate type axial plunger pump based on a rotary drive of a return disc according to the present invention.
Fig. 2 is an overall assembled partial cross-sectional view of a floating swash plate type axial plunger pump based on a rotary drive of a return disc according to the present invention.
Fig. 3 is an exploded view (de-housing) of a floating swash plate type axial plunger pump assembly based on a return disc rotational drive of the present invention.
Fig. 4 is a sectional view of a partial assembly structure of a floating swash plate type axial plunger pump cylinder body and a valve plate based on a rotary drive of a return plate of the present invention.
Fig. 5 is a rear view of a floating swash plate type axial plunger pump cylinder block structure based on a return disc rotation drive of the present invention.
FIG. 6 is a half cross-sectional view of a floating swash plate type axial plunger pump skid shoe, return plate, connecting pin and rotary plate subassembly based on the return plate rotational drive of the present invention.
FIG. 7 is a front view of a floating swash plate type axial plunger pump rotary disc structure based on rotary driving of the return disc of the present invention.
Fig. 8 is a rear view of a floating swash plate type axial plunger pump return disc structure based on a return disc rotation drive of the present invention.
FIG. 9 is a half cross-sectional view of a floating swash plate type axial plunger pump cylinder block structure based on a return disc rotational drive of the present invention.
Fig. 10 is a partial enlarged view of the position a in fig. 6.
Detailed Description
The invention will be further described with reference to the drawings and examples.
As shown in fig. 1, 2 and 3, the embodiment discloses a floating swash plate type axial plunger pump based on return disc rotation driving, which comprises a pump body 14, wherein the front side of the pump body 14 is a cavity opening of an inner cavity of the pump body 14, a front end cover 2 is arranged in the cavity opening, and the rear side of the pump body 14 is connected with a rear side cover 13. The bearing 3, the base 4, the sloping cam plate 5, the rotary disk 6, the return disk 9, the cylinder body 11 and the valve plate 12 are sequentially arranged behind the front end cover 2 in the inner cavity of the pump body 14. Wherein:
the axial directions of the front end cover 2, the bearing 3 and the base 4 are all the front and back directions, the front end of the outer ring of the bearing 3 is fixed on the rear side surface of the front end cover 2, and the front side of the base 4 is fixedly connected with the rear end of the outer ring of the bearing 3. The swash plate 5 is installed in the rear end of base 4 towards the front side of base 4 to the center pin of swash plate 5 is sharp acute angle for the straight line in fore-and-aft direction, still installs variable driving lever 15 in the pump body 14, and variable driving lever 15 is connected with the marginal spherical hinge of swash plate 5, promotes the inclination of swash plate variable driving lever 15 adjustable swash plate 5.
The rotary disk 6 has the same inclined posture as the swash plate 5, that is, the central axis of the rotary disk 6 has the same acute angle with respect to the straight line in the front-rear direction, and the front end surface of the rotary disk 6 is opposite to the rear end surface of the swash plate 5 and is in clearance fit. The return disc 9 and the rotary disc 6 have the same inclined posture, namely, the central axis of the return disc 9 forms the same acute included angle relative to the straight line in the front-back direction, and the front end surface of the return disc 9 is opposite to the rear end surface of the rotary disc 6 with a certain gap.
As shown in fig. 6 and 8, 9 pin mounting holes 22 are provided in the return disc 9, each pin mounting hole 22 is uniformly distributed in the return disc 9 in the circumferential direction around the center of the return disc 9, each pin mounting hole 22 is respectively provided with a connecting pin 16 in a penetrating manner, the pin mounting holes 22 are in clearance fit with the corresponding connecting pins 16, and each connecting pin 16 is respectively inserted into a hole in a corresponding position of the rotary disc 6 toward the front end of the rotary disc 6, so that the return disc 9 and the rotary disc 6 are integrally connected through the connecting pins 16.
The return disc 9 is further provided with a plurality of through holes at the circumferential periphery formed by the pin mounting holes 22, the through holes are uniformly distributed circumferentially around the center of the return disc 9, the sliding shoes 7 are respectively installed in the through holes in a penetrating manner, the rear ends of the sliding shoes 7, which face the cylinder 11, are respectively provided with ball sockets, and the front ends of the sliding shoes 7, which face the rotary disc 6, are respectively contacted with the rear end face of the rotary disc 6.
The axial direction of the cylinder body 11 is in the front-back direction, the center of the front end face of the cylinder body 11, which faces the rotary disc 6, is connected with a spherical hinge 8, the return disc 9 is sleeved on the spherical hinge 8 through a central through hole, and the central through hole of the cylinder body 11 is connected with the main shaft 1 through a spline 23. The cylinder block 11 has a plurality of cylinder bores 17 extending in the front-rear direction in the axial direction, and the cylinder bores 17 are uniformly distributed in the circumferential direction around the center axis of the cylinder block 11. Each cylinder hole 17 is slidably provided with a plunger 10, the front end of each plunger 10 penetrates from the cylinder 11 toward the front end face of the rotary disk 6, and the front end of each plunger 10 is hinged to the ball socket of the rear end of each shoe 7.
A central spring 27 is arranged between the cylinder body 11 and the spherical hinge 8, one end of the central spring 27 acts on the cylinder body 11 to enable the cylinder body 11 to press against the valve plate 12, the other end of the central spring 27 acts on the spherical hinge 8 to enable the spherical hinge 8 to press against the return disc 9, the return disc 9 presses against the sliding shoe 7 again, the sliding shoe 7 presses against the rotary disc 6 again, and finally the spring force is transmitted to enable the rotary disc 6 to press against the swash plate 5. The initial pre-compression, pre-sealing force before the pump starts and before the pressure builds is provided by the central spring 27 to the distribution pair formed between the cylinder block 11 and the distribution plate 12, the slipper pair formed between the slipper 7 and the rotary plate 6, and the rotary plate pair formed between the rotary plate 6 and the swash plate 5, respectively.
The axial direction of the valve plate 12 is the front-back direction, a plurality of flow distributing holes penetrating through the valve plate 12 from front to back are arranged in the valve plate 12, and the flow distributing holes are used for communicating the cylinder holes 17 and oil inlet and outlet ports of the pump body. The rear end face of the cylinder body 11 facing the valve plate 12 is in clearance fit with the front end face of the valve plate 12, the rear end face of the cylinder body 11 is provided with oil through holes 21 corresponding to the positions of the cylinder holes 17, and the oil through holes 21 are communicated with the corresponding cylinder holes 17.
The inner cavity of the pump body 14 is also provided with a main shaft 1 with the axial direction being the front-back direction, the main shaft 1 penetrates through the center of the front end cover 2, the inner ring of the bearing 3, the center of the base 4, the center of the swash plate 5, the center of the rotary disc 6, the center of the spherical hinge 8, the center of the cylinder body 11 and the center of the valve plate 12, and the main shaft 1 is connected with the cylinder body 11 and the spherical hinge 8 through splines, and the main shaft 1 is fixedly connected with the inner ring of the bearing 3. When the main shaft 1 rotates, the cylinder body 11 and the spherical hinge 8 integrally rotate along with the rotation, each plunger 10 installed in the cylinder hole 17 synchronously rotates along with the cylinder body 11, each corresponding sliding shoe 7 hinged with each plunger 10 synchronously rotates, the sliding shoes 7 drive the return disc 9 to synchronously rotate through the neck parts of the sliding shoes, and the return disc 9 synchronously rotates through the connecting pins 16 when in rotary motion, and the connecting pins 16 only bear radial force to drive the rotary disc 6 to rotate without influencing the assembly relation and the dynamics relation between the return disc 9 and the sliding shoes 7. The inner side surface of the swash plate 5 and the outer side surface of the rotary plate 6 are separated by a certain gap, namely, are not contacted radially. The rotary disk 6 rotates around the center thereof under the drive of the return disk 9, the rotary disk 6 and the return disk 9 synchronously rotate, and no relative sliding movement exists between the sliding shoe 7 and the rotary disk 6.
As shown in fig. 4, 5 and 9, the rear end face of the cylinder 11 is provided with oil storage tanks 25 corresponding to the inner side and the outer side of each oil passage hole 21, and each oil passage hole 21 is communicated with the corresponding two oil storage tanks 25 through damping holes 24. Each plunger 10 is provided with an oil guide through hole, the rear end of the oil guide through hole is communicated with a corresponding cylinder hole 17 in the cylinder body 11, and the front end of the oil guide through hole is communicated with a ball socket in the corresponding sliding shoe 7. The front end face of each shoe 7, which is in contact with the rotary disk 6, is provided with a hydrostatic oil chamber 26, respectively, and each hydrostatic oil chamber 26 communicates with a ball socket in the corresponding shoe 7, respectively.
As shown in fig. 7 and 10, oil guide channels 18 are provided in the rotary plate 6 corresponding to the respective shoes 7, and oil storage chambers 19 are provided in the rotary plate 6 corresponding to the respective oil guide channels 18 toward the front end surface of the swash plate 5. The rear ends of the oil guide channels 18 are respectively communicated with the static pressure oil chambers 26 of the corresponding sliding shoes 7, and the front ends of the oil guide channels 18 are respectively communicated with the oil storage oil chambers 19 of the front end face of the rotary disk 6. The front end face of the rotary disk 6 is also provided with two pressure relief ring grooves 20, wherein one pressure relief ring groove is positioned at the edge of the front end face of the rotary disk 6, and the other pressure relief ring groove is positioned in the ring formed by the oil storage oil chambers 19.
As a modification of the present embodiment, the oil storage chamber 19 may be provided on the rear end surface of the swash plate 5 facing the rotary disk 6, and the relief ring groove 20 may be provided on the rear end surface of the swash plate 5 facing the rotary disk 6.
In this embodiment, the oil enters the oil through holes 21 of the valve plate 12 into the oil through holes 21 of the cylinder 11 and then enters the cylinder holes 17 of the cylinder 11, or the oil flowing out of the cylinder holes 17 enters the valve plate 12 through the oil through holes 21, during which part of the oil in the oil through holes 21 flows into the oil storage tank 25 through the damping holes 24, and forms a second static pressure bearing under the action of the variable clearance fit between the rear end face of the cylinder 11 and the front end face of the valve plate 12. The friction and lubrication performance of the flow distribution pair can be improved and the friction and abrasion of the axial plunger pump at low speed can be reduced through the second static pressure support.
The oil that has entered the cylinder bore 17 passes through the oil passage holes of the plunger 10, the ball and socket of the shoes 7 and enters the hydrostatic chamber 26 of the shoes 7, whereby the oil forms a first hydrostatic bearing between each shoe 7 and the rotary disk 6. The oil entering the static pressure oil chamber 26 flows into the oil storage oil chamber 19 on the front end surface of the rotary disc 6 through the oil guide pore canal 18 in the rotary disc 6, and forms a third static pressure bearing in the gap between the rotary disc 6 and the swash plate 5 in cooperation with the oil drain ring groove 20. The first hydrostatic bearing and the third hydrostatic bearing cooperate to achieve complete hydrostatic bearing of the rotary disk 6.
The main shaft 1 drives the cylinder body 11 and the plunger 10 in the cylinder body 11 to move under the drive of the prime mover, when the cylinder body 11 rotates, the plunger 10 gradually extends outwards in the half cycle of the bottom-up rotation in the cylinder body 11, so that the volume of a cylinder hole 17 sealing working cavity of the cylinder body 11 is continuously increased, partial vacuum is generated, and hydraulic oil is sucked through a distributing hole on the distributing plate 12; conversely, when the plunger 10 gradually retracts into the cylinder body in the half cycle of the rotation from top to bottom, the volume of the sealed working cavity of the cylinder hole 17 is continuously reduced, namely, oil is pressed out outwards through the oil through hole 21 connected with the rear end of the cylinder hole 17 and the distributing hole on the distributing plate 12.
Each plunger 10 reciprocates once every revolution of the cylinder 11, and oil suction and pressure oil are completed once. Part of the oil in the oil passage opening 21 of the cylinder 11 flows into the oil storage tank 25 through the damping hole 24, and a second hydrostatic bearing is formed at the distributing pair by the variable clearance fit between the cylinder 11 and the distributing plate 12.
The sliding shoe 7 hinged with the plunger 10 drives the return disc 9 to rotate around the center line of the return disc, and the return disc 9 drives the rotary disc 6 to synchronously rotate through the connecting pin 16, so that no relative revolution sliding motion exists between the sliding shoe 7 and the rotary disc 6. The oil in the cylinder bore 17 passes through the oil passage hole of the plunger and the ball socket of the shoe 7 into the hydrostatic oil chamber 26 of the shoe 7, whereby a first hydrostatic bearing is formed between the shoe 7 and the rotary disk 6.
The oil in the static pressure oil chamber 26 enters the oil storage oil chamber 19 of the rotary disc 6 through the oil guide pore canal 18 in the rotary disc 6, and at this time, a third static pressure bearing is formed between the rotary disc 6 and the swash plate 5.
Because the sliding shoes 7 drive the return disc 9 to rotate through the neck part of the sliding shoes, the return disc 9 drives the floating rotary disc 6 which is completely supported by static pressure to rotate through the connecting pin 16, when the axial plunger pump works, no relative revolution motion exists between the sliding shoes 7 and the rotary disc 6, so that the overturning eccentric wear phenomenon of the sliding shoes 7 caused by centrifugal force is thoroughly eliminated, the friction power loss of sliding shoe pairs is eliminated, the 9 sliding shoe pairs scattered in the traditional axial plunger pump are converted into an integral rotary disc rotary pair between the rotary disc 6 and the swash plate 5, the integral rotary disc rotary pair performs rotary motion on the inclined disc surface around the central axis of the rotary disc rotary pair, centrifugal forces in the radial direction offset each other, the stability and the reliability of the rotary motion are improved, the total contact area between the rotary disc 6 and the swash plate 5 is obviously increased compared with that of the 9 scattered sliding shoe pairs of the traditional axial plunger pump, and the PV value is obviously reduced, and the pump is beneficial to realizing high speed.
The preferred embodiments of the present invention have been described in detail above with reference to the accompanying drawings, and the examples described herein are merely illustrative of the preferred embodiments of the present invention and are not intended to limit the spirit and scope of the present invention. The individual technical features described in the above-described embodiments may be combined in any suitable manner without contradiction, and such combination should also be regarded as the disclosure of the present invention as long as it does not deviate from the idea of the present invention. The various possible combinations of the invention are not described in detail in order to avoid unnecessary repetition.
The present invention is not limited to the specific details of the above embodiments, and various modifications and improvements made by those skilled in the art to the technical solution of the present invention should fall within the protection scope of the present invention without departing from the scope of the technical concept of the present invention, and the technical content of the present invention is fully described in the claims.
Claims (5)
1. The utility model provides a floating swash plate type axial plunger pump based on return disc rotary drive, including pump body (14), be equipped with main shaft (1) in pump body (14), and along the distribution plate (12), cylinder body (11), rotary disk (6), sloping cam plate (5) of straight line distribution in proper order, install spherical hinge (8) towards the terminal surface center of rotary disk (6) in cylinder body (11), be equipped with a plurality of cylinder bores (17) in cylinder body (11), slidable mounting has plunger (10) in every cylinder bore (17) respectively, each plunger (10) one end is worn out from cylinder body (11) towards the terminal surface of rotary disk (6) one end respectively, the terminal surface of cylinder body (11) towards the terminal surface of rotary disk (12) is equipped with the oil orifice (21) of a plurality of one-to-one intercommunication cylinder bores (17), be equipped with a plurality of water flow holes that link up in distribution plate (12), characterized in that rotary disk (6) are equipped with round trip plate (9) towards the one side of cylinder body (11), there are a plurality of connecting pins (16) in trip plate (9), each connecting pin (16) are towards rotary disk (6) one end of respectively;
a plurality of through holes are formed in the return disc (9), sliding shoes (7) are respectively arranged in each through hole in a penetrating mode, ball sockets are respectively arranged at one end, facing the cylinder body (11), of each sliding shoe (7), one end, penetrating out of the cylinder body (11), of each plunger (10) is hinged into the ball socket of each sliding shoe (7) in a one-to-one correspondence mode, and the other end of each sliding shoe (7) is in contact with a corresponding surface of the rotary disc (6);
the return disc (9) is also in contact with the spherical hinge (8) through a central through hole of the main shaft (1), the main shaft (1) sequentially penetrates through the center of the valve plate (12), the center of the cylinder body (11), the center of the spherical hinge (8), the center of the rotary disc (6) and the center of the swash plate (5), and the main shaft (1) is connected with the cylinder body (11) and the spherical hinge (8), so that the cylinder body (11) and the spherical hinge (8) integrally rotate along with the main shaft (1) when the main shaft (1) rotates, the return disc (9) rotates, the sliding shoes (7) and the plungers (10) rotate, the rotary disc (6) is driven to rotate through the connecting pins (16) when the return disc (9) rotates, and the side surfaces of the rotary disc (6) and the swash plate (5) are in clearance fit, namely are not in radial contact;
the plunger piston is characterized in that an oil guide through hole is formed in each plunger piston (10), one end of the oil guide through hole is communicated to a corresponding cylinder hole (17), the other end of the oil guide through hole is communicated to a ball socket in a corresponding sliding shoe (7), a static pressure oil chamber (26) is formed in the end face of one end, in contact with a rotary disc (6), of each sliding shoe (7), each static pressure oil chamber (26) is communicated with the ball socket in the corresponding sliding shoe (7), oil entering the cylinder hole (17) of a cylinder body (11) from a valve plate (12) enters the static pressure oil chamber (26) of the sliding shoe (7) through the oil guide through hole of the plunger piston (10) and the ball socket of the sliding shoe (7), and therefore first static pressure bearings are formed between each sliding shoe (7) and the rotary disc (6) through the oil.
2. The floating swash plate type axial plunger pump based on the return disc rotation driving according to claim 1, wherein one end face of the cylinder body (11) facing the valve plate (12) is in clearance fit with the valve plate (12), an oil storage groove (25) is respectively arranged at the position, corresponding to each oil through hole (21), of one end face of the cylinder body (11) facing the valve plate (12), the oil storage groove (25) is respectively communicated with the corresponding oil through hole (21) through a damping hole (24), part of oil in the oil through holes (21) enters the oil storage groove (25) through the damping hole (24), and then flows into a clearance between the cylinder body (11) and the valve plate (12) to form a second hydrostatic bearing.
3. The floating swash plate type axial plunger pump based on the return rotation driving according to claim 1, wherein the rotary disc (6) is in clearance fit with the swash plate (5), oil guide holes (18) are respectively formed in the rotary disc (6) corresponding to the positions of each sliding shoe (7), one ends of the oil guide holes (18) are respectively communicated with static pressure oil chambers (26) of the corresponding sliding shoes (7), the other ends of the oil guide holes (18) are respectively communicated to the clearance between the rotary disc (6) and the swash plate (5), and therefore oil in the static pressure oil chambers (26) flows into an oil storage oil chamber (19) between the rotary disc (6) and the swash plate (5) through the oil guide holes (18), and a third static pressure bearing is formed.
4. A floating swash plate type axial plunger pump based on return rotation driving according to claim 3, characterized in that the surface of the rotary disc (6) facing the swash plate (5) is respectively provided with an oil storage oil chamber (19) corresponding to each oil guide hole (18), the other ends of the oil guide holes (18) are respectively communicated with the corresponding oil storage oil chambers (19), and oil flows into a gap between the rotary disc (6) and the swash plate (5) through the oil storage oil chambers (19) to form a third hydrostatic bearing.
5. The floating swash plate type axial plunger pump based on the return rotation driving according to claim 4, wherein the side of the rotary disc (6) facing the swash plate (5) is further provided with a pressure relief ring groove (20).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310479210.2A CN117006010A (en) | 2023-04-28 | 2023-04-28 | Floating swash plate type axial plunger pump based on return disc rotation driving |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310479210.2A CN117006010A (en) | 2023-04-28 | 2023-04-28 | Floating swash plate type axial plunger pump based on return disc rotation driving |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117006010A true CN117006010A (en) | 2023-11-07 |
Family
ID=88560778
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310479210.2A Pending CN117006010A (en) | 2023-04-28 | 2023-04-28 | Floating swash plate type axial plunger pump based on return disc rotation driving |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117006010A (en) |
-
2023
- 2023-04-28 CN CN202310479210.2A patent/CN117006010A/en active Pending
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CA1254523A (en) | Slant plate type hydraulic device | |
| CN103184990B (en) | Oblique plunger type pure water hydraulic swash plate pump | |
| CN101832243A (en) | Axial water pressure plunger pump with easy maintenance | |
| CN111692063A (en) | Floating swash plate follow-up spherical hinge hinged conical plunger variable pump/motor rotating assembly | |
| CN204493093U (en) | The split type return plate of a kind of self contering antidumping | |
| CN101949374A (en) | Swash plate type valve distributing high-pressure pure water plunger pump | |
| CN109653973B (en) | Water lubrication shaft valve composite flow distribution radial plunger pump | |
| CN201786591U (en) | Axial water-pressure plunger pump easy to be repaired | |
| CN110748468B (en) | High-speed high-pressure axial plunger pump | |
| CN209761643U (en) | Flow distribution sliding disc pair and plunger pump or motor comprising same | |
| CN209855979U (en) | Axial plunger pump or motor | |
| CN117006010A (en) | Floating swash plate type axial plunger pump based on return disc rotation driving | |
| US3007420A (en) | Hydraulic pump or motor | |
| CN214221414U (en) | Balanced opposition sliding plate formula axial plunger pump or motor | |
| US3793923A (en) | Radial piston hydraulic machines | |
| CN114263584A (en) | Tandem piston pump | |
| CN209761644U (en) | Sliding disc supporting type through shaft plunger pump or motor | |
| JPH0626447A (en) | Hydraulic pump motor | |
| CN111140564A (en) | Blade swing hydraulic cylinder with floating side plates and floating blades | |
| CN211950761U (en) | Axial plunger device for sliding shoes and swash plates | |
| CN214660670U (en) | Axial plunger pump or motor | |
| CN117006038B (en) | Double-oil-distribution double-oil-outlet self-priming plunger pump | |
| CN219220653U (en) | Kinematic pair structure, sliding disc pair structure and sliding disc type plunger pump or motor | |
| CN221074516U (en) | Friction pair structure of medium-high pressure plunger pump | |
| CN215762063U (en) | Swash plate structure of oil film lubrication and floating support |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |