EP2012010A1 - Pompe ou moteur a pistons axiaux - Google Patents

Pompe ou moteur a pistons axiaux Download PDF

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Publication number
EP2012010A1
EP2012010A1 EP07720394A EP07720394A EP2012010A1 EP 2012010 A1 EP2012010 A1 EP 2012010A1 EP 07720394 A EP07720394 A EP 07720394A EP 07720394 A EP07720394 A EP 07720394A EP 2012010 A1 EP2012010 A1 EP 2012010A1
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EP
European Patent Office
Prior art keywords
swash plate
disk
main shaft
pendulous
plunger
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.)
Withdrawn
Application number
EP07720394A
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German (de)
English (en)
Inventor
Ronghui Zhu
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Individual
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Individual
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Publication date
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Publication of EP2012010A1 publication Critical patent/EP2012010A1/fr
Withdrawn legal-status Critical Current

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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
    • F04B1/128—Driving means
    • 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
    • F04B1/124—Pistons
    • 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
    • F04B1/14—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 having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2035—Cylinder barrels
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2042—Valves
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • F04B1/2085—Bearings for swash plates or driving axles

Definitions

  • the present invention relates to a hydraulic pump or motor device, particularly to an axial plunger pump or motor.
  • a hydraulic pump or motor In hydraulic mechanisms, a hydraulic pump or motor is the heart of the hydraulic device. Theoretically, a hydraulic pump and a motor are switchable, except for some difference in some parts. Therefore, the description of the invention will only focus on the design of the pump, and the structure of a motor will be omitted in that it is similar to that of the pump. Plunger pumps have been increasingly widely employed in engineering mechanisms due to their high efficiency, adaptation to high pressure and aptness to carry out variable displacement adjustment.
  • the plunger pump can be classified into two categories according to the stroke direction of the plunger, that is, an axial plunger pump and an axial plunger pump. Furthermore, the axial plunger pump may be classified into a swash plate plunger pump and a bent axis plunger pump, according to the mechanism of motion transition. The structural characteristics of these two kinds of pumps are referred to Figs. 1 through 3 , respectively.
  • Such an axial plunger pump of a swash plate type is a variable displacement pump of high pressure, high speed, high impact resistance and high integration degree.
  • a rotor is driven to rotate by the main shaft through involute splines.
  • a plurality of plungers which are uniformly distributed in the rotor, press the sliding tracks of the plunger assemblies against the plane of the frictional plate of the swash plate through a ball joint and a press plate. Since there forms an angle between the swash plate plane and the rotation axis, the plunger body not only rotates with the rotor, but also reciprocates along the plunger hole of the rotor. In this way, the plunger pump carries out oil intaking and supplying.
  • the stroke of the plunger can be changed through adjusting the inclination angle of the swash plate, so as to perform variable displacement adjustments.
  • Changing the inclination angle of the swash plate leads to variations of the flow direction of the pressurized oil, or the rotation direction of the rotor in case of serving as a hydraulic motor.
  • an axial plunger pump of a swash plate type In such an axial plunger pump of a swash plate type, it is easy to perform variable displacement adjustments, and convenient to change the direction of the pressurized oil and the rotation direction of the rotor and to switch between the pump state and the motor state. Its cost is low, with relatively simple structure and small volume.
  • an axial plunger pump of a swash plate type has three friction pairs, i.e., a pair between rotor and oil-distributing plate, a pair between plunger and plunger hole, and a pair between plunger sliding track and swash plate. In the friction pair between plunger and plunger hole, an individual plunger is not only subject to an axis force, but also to a tangential force and a torque.
  • such a pump has three disadvantages, (i) the overall efficiency is relatively low, wherein the volume efficiency of the oil pump is between 0.92 and 0.98 and the mechanical efficiency is between 0.90 and 0.95, and the overall efficiency is not higher than 0.95; (ii) it is susceptible to staining from oil and liquid, thus resulting in a short pump service life; (iii) the allowable rotation speed is not high.
  • a bent axis plunger pump As shown in Fig. 3 , the working principle of a bent axis plunger pump is fairly similar to that of a swash plate pump. However, they have large differences in structure, and they also have different force profiles.
  • the method of articulating the ball head of the plunger is substituted for the approach of employing a sliding track and a swash plate in a swash plate pump, such that the structural strengthen and the impact resistance are improved.
  • the pump is operating, since the angle between the axis of the linking rod and the axis of the plunger is small, the lateral pressure between the plunger and the cylinder wall is much smaller than in the case of a swash plate pump.
  • the inclination angle ⁇ may also be increased to 25 through 30 degrees (less than 20 degrees in case of a swash plate pump), such that the variation range of flow flux is enlarged.
  • the drive shaft of a bent axis pump is small in dimension, or it does not penetrate through the oil-distributing disk, such that the rotor diameter of the cylinder is correspondingly reduced.
  • leakage and loss due to friction are decreased, resulting in a higher overall efficiency than that of the swash disk pump, e.g., higher by 2-3% under the same technical level.
  • the pump performance in oil-intaking is thus improved since the circumferential speed of the oil cylinder is decreased, and the rotation speed limit of the pump can therefore be increased.
  • the requirement on the accuracy of oil-filtering in a bent axial pump is low, e.g., generally 25m, with comparison of 10 to 15m in a swash plate pump.
  • bent axis pumps have been increasingly employed in the hydraulic mechanisms.
  • a pump carries out variable displacement through cylinder swinging, and the profile dimension is large.
  • the inclination of the rotor and the power shaft makes the profile form a corner shape, which is not desirable in situations of narrow space or in case where coaxial assemble is required.
  • structure and technical requirements are complicated, thus leading to a high cost.
  • the object of the invention is to provide an axial plunger pump or motor, which increases the efficiency of the plunger pump or motor, has a simplified structure, a decreased volume, a lower cost, and a wide application range, and particularly is applicable to situations where special installation requirements should be meet, such as in transmissions of motor vehicles.
  • an axial plunger pump or motor comprising a casing; a main shaft rotatably supported on the casing; a rotor cylinder with a plurality of plunger holes, which is coupled to the main shaft and is driven to rotate about the main shaft axis by the main shaft and which has an oil-distributing end surface; an oil-distributing disk in cooperation with the oil-distributing end surface of the rotor cylinder; a rotary swash plate whose end surface is disposed in a manner axially opposing the plurality of plunger holes of the rotor cylinder and which can rotate about the swash plate axis forming an angle with respect to the main shaft axis; a plurality of plunger assemblies, an end of each being articulated to an end surface of the rotary swash plate and another end of each being slidably disposed in the plunger holes of the rotor cylinder; a constant velocity universal coupling which is provided between the
  • said constant velocity universal coupling may be a Rzeppa constant velocity universal coupling, a half angular Rzeppa constant velocity universal coupling, a ball joint constant velocity universal coupling or a Weiss constant velocity university coupling.
  • the Rzeppa constant velocity universal coupling in the invention comprises an inner race ring with an outer raceway, an even number of steel balls, a holder and an outer race ring with an inner raceway, wherein said steel balls are arranged on the holder and are located in the inner raceway and the outer raceway, said inner race ring is coupled to the main shaft, said outer race ring is coupled to the rotary swash plate, such that the main shaft and the rotary swash plate are respectively rotated about the main shaft axis and the swash plate axis via the Rzeppa constant velocity universal coupling.
  • said outer race ring may be integrally formed on the rotary swash plate.
  • said rotary swash plate may be supported on the casing via a swash plate bearing.
  • said rotary swash plate is supported on a pendulous disk via a swash plate bearing
  • the pendulous disk is supported on said casing via a pendulous disk bearing
  • the rotation axis of the pendulous disk bearing is perpendicular to the main shaft axis and passes through the center of the constant velocity universal coupling.
  • said pendulous disk may be connected with a variable displacement adjustment mechanism for adjusting the deflection angle of the pendulous disk, such that the angle between the swash plate axis of the pendulous disk supported thereon and the main shaft axis is adjusted through changing the deflection angle of the pendulous disk, and therefore the strokes of the plunger assemblies are changed so as to carry out variable displacement adjustments.
  • variable displacement adjustment mechanism in the invention is a variable displacement oil tank, the piston of which is connected to the pendulous disk so as to drive the pendulous disk to deflect through extending and retracting of the piston.
  • variable displacement adjustment mechanism is a variable displacement adjustment mechanism of a trunnion type, which includes a trunnion connected to the pendulous disk and a driving mechanism for driving the trunnion to rotate, the rotation axis of the trunnion is identical to the rotation axis of the pendulous disk so as to drive the pendulous disk to deflect through the trunnion.
  • said rotor cylinder is in a conic shape, the diameter thereof at the end closer to the rotary swash plate is larger than that at the other end.
  • the plurality of plunger holes on said rotor cylinder are also distributed in a conic form, wherein the diameter of the circle in which the plunger hole center at the end in corporation with the plunger assemblies lies is larger than that at the other end.
  • said plunger assembly may particularly be a plunger assembly of a ball joint type, which comprises a plunger and a ball-headed rod with both ends thereof being in a ball head shape, said rotary swash plate is provided with a socket, a ball-headed end of the ball-headed rod is located in the socket to form a ball-joint connection with the pendulous disk, and the other end thereof is located in the plunger to form a ball-joint connection with the plunger, and the plunger is slidably provided in the plunger hole.
  • the plunger port in communication with the plunger holes to introduce pressurized oil to lubricate the ball head at the both ends.
  • the articulation centers of said plurality of plunger assemblies on the pendulous disk are located in a same plane, and the intersection point of the plane with the main shaft axis is identical to the center of the constant velocity universal coupling.
  • said rotary swash plate is provided with an oil-distribution disk at the rear end thereof, the rotor cylinder is axially positioned along the main shaft through a pressure spring and a pressure spring stop collar, the end of the main shaft is provided with an oil port and a radial oil pathway, such that the pressure between the rotor cylinder and the oil-distribution disk is adjusted through introducing pressurized oil into the radial oil pathway.
  • the oil-distribution end surface of said rotor cylinder may be a spheric surface, said oil-distribution disk forms a spheric corporation with the oil-distribution end surface.
  • said swash plate bearing is a combination bearing of a needle bearing and a cylinder or a cone roller push bearing.
  • the pendulous disk bearing is a needle bearing in a crescent form.
  • the axial plunger pump or motor according to the invention may drive, via the constant velocity universal coupling, the rotary swash plate to rotate about the swash plate axis forming an angle with respect to the main shaft axis, while at the same the main shaft drive the rotary cylinder to rotate.
  • the plunger assemblies reciprocate in the plunger holes of the rotor cylinder, causing volume variations in the cylinder, and communicates with the inlet port 13 and the outlet port 20 sequential via the cooperation with the oil-distributing disk.
  • oil-intaking and oil-extruding are carried out, or in other words, transition between rotation mechanical energy and hydraulic energy is achieved.
  • the inclination angle of the rotary swash plate may be changed through driving the pendulous disk to swing by the variable displacement mechanism, so as to conveniently perform variable displacement adjustments.
  • the axial plunger pump or motor according to the present invention has the following effects.
  • an axial plunger pump or a motor mainly includes a casing 1, a main shaft 4 rotatably supported on the casing 1, a rotor cylinder 14 with a plurality of plunger holes which is coupled to the main shaft 4 and is driven to rotate about the main shaft axis 41 by the main shaft 4 and which has an oil-distributing end surface, an oil-distributing disk 15 in cooperation with the oil-distributing end surface of the rotor cylinder 14, a rotary swash plate 9 whose end surface is disposed in a manner axially opposing the plurality of plunger holes of the rotor cylinder 14 and which may rotate about the swash plate axis 91 forming an angle with respect to the main shaft axis, a plurality of plunger assemblies 10, an end of each articulated to an end surface of the rotary swash plate 9 and another end of each slidably disposed in the plunger holes of the rotor cylinder 14, a constant velocity universal coupling 11 which is provided between the rotary swash plate
  • the main shaft 4 is driven to rotate about the main shaft axis 41, and the rotary swash plate 9 is driven, by constant velocity universal coupling 11, to rotate about the swash plate axis 91 forming an angle with respect to the main shaft axis 41.
  • the plunger assemblies 10 reciprocate in the plunger holes of the rotor cylinder 14, causing volume variations in the rotor cylinder 14 to carry out oil-intaking and oil-extruding, or in other words, transition between rotation mechanical energy and hydraulic energy is achieved.
  • the rotary swash plate 9 rotates about the swash plate axis 91 by the hydraulic oil in the plunger holes so as to drive the main shaft 4 to rotate about the main shaft axis 41 via the constant velocity universal coupling 11 and to drive the rotor cylinder 14 coupled with the main shaft 4 to rotate.
  • the plunger assemblies 10 reciprocate in the plunger holes, such that hydraulic energy is transited to rotary mechanical energy of the main shaft.
  • the casing 1 and a rear end cap 18 are connected to each via screws so as to form a closed box, and the main shaft 4 is supported in the box via a front bearing 6 and a rear bearing 16, as shown in Figs. 4 to 7 .
  • An inlet slot and an outlet slot in the oil-distributing disk 15 are communicated with an inlet port 13 and an outlet port 20, respectively.
  • the main shaft 4 penetrates through the oil-distributing disk 15, the rotor cylinder 14, a pressure spring 19, the constant velocity universal coupling 11 and the rotary swash plate 9, in this order, and projects through an end seal cap 5 from a side of the box.
  • the rotor cylinder 14 is circumferentially fixed to the main shaft 4 via a spline, and is pressed against the oil-distributing disk 15 by the pressure spring 19 surrounding the main shaft 4 so as to achieve an initial seal between the rotor cylinder 14 and the oil-distributing disk 15.
  • the rotating main shaft 4 drives rotary swash plate 9 to rotate about the swash plate axis 91 via the constant velocity universal coupling 11, while at the same time driving the rotor cylinder 14 to rotate via the spline.
  • the plunger assemblies 10 are driven to reciprocate in the plunger holes in the rotor cylinder 14, causing volume variations in the plunger holes.
  • These plunger holes communicates with the inlet port 13 and the outlet port 20 sequential via the cooperation with the oil-distributing disk 15. In this way, oil-intaking and oil-extruding are conducted, i.e., transition between rotation mechanical energy and hydraulic energy is achieved.
  • the constant velocity universal coupling 11 may be a Rzeppa constant velocity universal coupling, a half angular Rzeppa constant velocity universal coupling, a ball joint constant velocity universal coupling or a Weiss constant velocity university coupling.
  • the invention takes a Rzeppa constant velocity universal joint as an example and gives a detailed explanation thereof.
  • Other types of constant velocity universal joints such as a half angular Rzeppa constant velocity universal coupling, a ball joint constant velocity universal coupling, a Weiss constant velocity university coupling, and the like, are also applicable if dimensions of space permit, even though their structures are relatively complicated as compared to the structure of a Rzeppa constant velocity universal joint . Therefore detailed explanations thereof are omitted. As shown in Figs.
  • the constant velocity universal coupling 11 in an example where the constant velocity universal coupling 11 is a Rzeppa constant velocity universal joint, it comprises an inner race ring 111 with an outer raceway, an even number of steel balls 112, a holder 113 and an outer race ring 114 with an inner raceway, wherein the outer race ring 114 is coupled to the rotary swash plate 9 and the inner race ring 111 is coupled to the main shaft 4, such that the main shaft 4 can drive the rotary swash plate 9 which is coupled to the outer race ring 114 to rotate about the swash plate axis 91 forming an angle with respect to the main shaft axis 41 while at the same time driving the inner race ring 111 (i.e., the rotation axis about which the outer race ring 114 rotates) to rotate about the main shaft axis 41.
  • the inner race ring 111 i.e., the rotation axis about which the outer race ring 114 rotates
  • the inner holes of the outer race ring and the rotary swash plate 9 may be combined so as to integrate the outer race ring 114 with the rotary swash plate 9, thus space effectiveness in the radial direction is ensured.
  • the inner race ring 111 and the main shaft 4 may also be combined such that the inner race ring 111 is integrated with the main shaft 4, they are provided separately in consideration of manufacture process and installation feasibility, e.g., the inner race ring 111 is circumferentially fixedly coupled to the main shaft 4 via a spline and is restrained in the axial direction by a stop collar 21 on the shaft. As shown in Fig.
  • the sphere centers of both the inner race ring and the outer race ring should be arranged on the main shaft axis 41 and be located on each side of the center of the constant velocity universal joint coupling 11 with the distances thereto being equal.
  • the holder 113 confines the even number of steel balls 112 in a same plane which also passes through the center of the coupling.
  • the plurality of plunger assemblies 10 in the invention may be plunger assembles of a ball joint type, which comprises a plunger and a ball-headed rod with both ends thereof being in a ball head shape and which is provided with an oil port for introducing pressurized oil to lubricate the ball head at the both ends.
  • the structure of the plunger assemblies 10 is the same as the structure of the plunger assemblies of the bent axis pump. Uniformly distributed on the right end of the rotary swash plate 9 are a plurality of sockets with their centers located in a same plane.
  • the ends of ball heads of the plunger assemblies 10 are imbedded into the sockets of the rotary swash plate 9 and restrained therein by a retainer plate 23, and the plunger ends of the plunger assemblies 10 projects into the plunger holes of the rotor cylinder 14.
  • the number of the plunger assemblies 10 is equal to the number of the sockets in the rotary swash plate 9 and the number of plunger holes in the rotor.
  • the central point of the constant velocity universal coupling 11 is coincident with the intersection point of the central plane of the plurality of sockets in the rotary swash plate 9 with the main shaft axis.
  • the middle case of casing 1 and the front end cap may be an integral structure cast from cast iron or die-cast from aluminum alloy, while the rear end cap 18 is connected to the middle case via screws.
  • the middle case and the front end cap are not an integral structure and they are coupled with each other via screws.
  • the integral structure presents strength, but it is more difficult to process, contrary to the latter case.
  • the axial plunger pump or motor according to the invention may carry out variable adjustments.
  • the rotary swash plate 9 is embedded into a pendulous disk 7 via a swash plate bearing 8 which can receive a radial force, an axial force and a torque at the same time.
  • the pendulous disk 7 is supported to the casing 1 via a pendulous disk bearing 2.
  • the rotation axis of this pendulous disk bearing 2 is perpendicular to the main shaft axis 41 and passes through the center of constant velocity universal coupling 11.
  • the pendulous disk 7 can only swing about the center of constant velocity universal coupling 11 in a plane parallel to the main shaft axis 41.
  • the inclination angle of the rotary swash plate 9 i.e., the inclination angle of the swash plate axis 91 with respect to the main shaft axis 41
  • the pendulous disk 7 may be connected with a variable displacement adjustment mechanism for adjusting the deflection angle of the pendulous disk 7.
  • the constant velocity universal coupling 11 transfers the rotation motion of main shaft 4 and thus the moment to the rotary swash plate 9 rotating about the swash plate axis 91, therefore it is very convenient to carry out variable displacement adjustment of a pump or motor through driving, via the variable displacement adjustment mechanism, the pendulous disk 7 to swing so as to change the inclination angle of the rotary swash plate 9.
  • the pendulous disk 7 comprises an upper partial cylinder and a lower partial cylinder, and is supported to the casing 1 via the pendulous disk bearing 2, with its right end provided with an inner cylinder surface of a step shape for the swash plate bearing to be embedded.
  • the variable adjustment mechanism may be an adjustment mechanism of a trunnion type which conducts adjustment from outside. It includes a trunnion 24 connected to the pendulous disk 7 and a driving mechanism for driving the trunnion 24 to rotate.
  • the rotation axis of the variable displacement trunnion 24 is identical to the swing axis. In this way, the variable displacement adjustment is achieved through the peripherally provided driving mechanism driving the trunnion 24 to rotate.
  • at one side of the pendulous disk 7 may be provided with a seat 26 for the variable displacement trunnion via a threaded member 27.
  • the variable displacement trunnion 24 is circumferentially fixedly connected to the trunnion seat 26 via a spline or a flat key so as to install the variable displacement trunnion 24 to the pendulous disk 7.
  • variable displacement mechanism may also includes a variable displacement oil tank 28, the piston of which is connected to the pendulous disk 7 so as to drive the pendulous disk 7 to deflect through extending and retracting the piston so as to carry out variable displacement adjustment.
  • the variable displacement adjustment mechanism may certainly assume other forms, for example, they may take use of variable displacement mechanism of various swash plate pumps, only if the deflection angle of the pendulous disk 7 can be changed by means of the variable displacement mechanisms. Herein explanations thereof are omitted.
  • the swash plate bearing 2 in the embodiment 1 may be two needle bearings in a crescent form which are longitudinally symmetrcial.
  • the rotation axis of the bearing 2 is perpendicular to the main shaft axis 4 and passes through the center of the constant velocity universal coupling 11.
  • the outer race ring of the bearing is fixed to the bearing seat of the casing 1, and the inner race ring thereof is fixed to the cylindrical surface of the pendulous disk 7 on the left side or is integral with the cylindrical surface.
  • the function of the bearing is to transfer the push force acted upon the pendulous disk 7 to the casing 1 and to suppress the swinging resistance to the pendulous disk 7.
  • the bearing may be other types of bearing, such as a sliding bearing.
  • the rotary swash plate 9 may be provided with a flare-shaped inner hole at its left end.
  • the main shaft 4 passes through this inner hole, and does not interfere with the rotary swash plate 9 when the rotary swash plate 9 is swinging with the pendulous disk 7.
  • the rotary swash plate 9 is also provided with an outer cylinder surface at its left end so as to install the swash plate bearing 8.
  • the rotary swash plate 9 has a plurality of sockets on its right end surface, the centers of which sockets are located in a same plane. Generally, the number of the sockets are odd, such as 5, 7, ..., 11.
  • the rotary swash plate 9 is provided with a spherical hole, and there is engraved an inner raceway along the direction of the main shaft 4, as the out race ring of the constant velocity universal coupling 11.
  • the axial plunger pump or motor may be applicable to a constant displacement pump. Since no variable displacement adjustment is needed, the pendulous disk 7, the pendulous disk bearing 2 and the variable displacement mechanism can be dispensed with and the rotary swash plate 9 can be directly supported at the oblique surface of the casing 1, such that the whole structure is very simple and compact.
  • the important friction surface may be subject to plating or coating, for example, molybdenum disulfide plating so as to decrease friction loss and improve efficiency and service life.
  • the swash plate bearing 8 of the invention will receive an axial force, a radial force and a rolling torque from the swash plate.
  • a needle/cylinder (cone) roller push bearing may be employed as the bearing 8, and other types of bearings or combination bearings are also applicable if only they can perform the same functions.
  • the main shaft 4 is provided with a spline or a flat key at its front end so as to be connected to other motive machines or working machines.
  • main shaft 4 On the middle of main shaft 4 are provided with splines to be circumferentially fixedly connected to the constant velocity universal coupling 11 and rotor cylinder 14, respectively, so as to drive the rotary swash plate 9 and the rotor cylinder 14 to rotate and to transfer torques.
  • a disk pressure spring 19 At the middle of the main shaft 4 is supported a disk pressure spring 19 with a stop collar 21 and a pressure spring seat.
  • the pressure spring 19 may also be a cylinder-shaped coil spring.
  • a residual pressure method is employed to calculate the pre-compression force, with the principle being to ensure reliable seal between the rotor cylinder 14 and the oil-distributing disk 15.
  • the right end of the main shaft 4 is provided with an oil hole and a radial oil pathway, such that the pressurized oil introduced from the outside of the pump acts upon the right end surface of the rotor cylinder 14.
  • the pressure between the rotor cylinder 14 and the oil-distributing disk 15 may be adjusted through adjusting the pressure of the pressurized oil from outside. In this way, the pressure between the rotor cylinder 14 and the oil-distributing disk 15 can be conveniently adjusted to ensure a higher efficiency of the pump under various working conditions.
  • the rotor cylinder 14 in the invention is a cylinder with a plurality of plunger holes arranged uniformly in the circumferential direction. These plunger holes are in a close active corporation with the plungers of the plunger assemblies 10.
  • the oil-distribution end surface of the rotor cylinder 14 is a spheric surface, which is in a close corporation with the spheric oil-distributing disk 15, thus generating a spheric corporation therebetween and presenting a good self-centering characteristics.
  • the rotor cylinder 14 may be made of such materials as copper, nodular cast iron, cast iron, forged steel, etc.
  • the inner surface of the plunger holes and the spheric oil-distribution surface are subject to the treatment (such as embedding and plating) to decrease friction and enhance wear resistance. Since the constant velocity universal coupling 11 should be installed at the center of the rotary swash plate 9, the radial dimension thereof will consequentially be increased in case of the pump of small displacement.
  • the rotor cylinder 14 may be formed in a conic shape, that is, its diameter on the left end is larger than its diameter on the right end.
  • the plurality of plunger holes are shaped in a conic form, wherein, the diameter of the circle in which the plunger hole center at the end (in the left of the drawing) in corporation with the plunger assemblies 10 lies is larger than that at the other end (in the right of the drawing). In this way, it is not necessary to increase the diameter of the rotor cylinder 14 on the whole, and it is possible to decrease the diameter of the oil-distribution hole. As shown in Fig. 4 , the oil-distribution end surface of the rotor cylinder 14 may be in a planar form, such that the process is easy.
  • variable displacement pump as described in the embodiment 1 according to the invention, which has a displacement of 16 I/r and a rating pressure of 35MPa.
  • each plunger has an effective volume of 2.3ml.
  • the maximal stroke of the piston is 1.8cm to 2.0cm, and the diameter of the plunger is 12mm to 13mm.
  • the diameter of the circle in which the plunger center lies is dependent on the swinging angle of the pendulous disk 7.
  • the swinging angle is chosen to be 20 degrees according to experience, such that the diameter of said circle should be 56mm.
  • the outer diameter of the rotor cylinder 14 is 75mm ⁇ 40mm.
  • the rating output torque of the pump is 89Nm, therefore, the diameter of the power shaft (main shaft 4) which employs simple steel is only between 15mm and 20mm.
  • the rotor cylinder 14 is formed in a conic shape, the rotor diameter at the larger end being 82mm and that at the smaller end being 72mm.
  • the rotary swash plate 9 has a diameter of 85mm, and the diameter of pendulous disk 7 has a diameter of 100mm.
  • the dimension of the whole pump is 120mm ⁇ 150mm (the extension length of the shaft end not included).
  • the dimension and the weight are smaller than those of the swash plate pump with the same displacement, and are even much smaller than those of the bent axis pump.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP07720394A 2006-03-14 2007-03-13 Pompe ou moteur a pistons axiaux Withdrawn EP2012010A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN200620007920 2006-03-14
PCT/CN2007/000807 WO2007104257A1 (fr) 2006-03-14 2007-03-13 Pompe ou moteur a pistons axiaux

Publications (1)

Publication Number Publication Date
EP2012010A1 true EP2012010A1 (fr) 2009-01-07

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EP07720394A Withdrawn EP2012010A1 (fr) 2006-03-14 2007-03-13 Pompe ou moteur a pistons axiaux

Country Status (6)

Country Link
US (1) US20090007773A1 (fr)
EP (1) EP2012010A1 (fr)
JP (1) JP2009529619A (fr)
KR (1) KR20090020549A (fr)
CN (1) CN101415944B (fr)
WO (1) WO2007104257A1 (fr)

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WO2012150069A1 (fr) * 2011-05-02 2012-11-08 Zf Friedrichshafen Ag Machine à pistons axiaux à axe incliné
EP3438451A4 (fr) * 2016-03-28 2019-10-30 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Machine rotative hydraulique
US10830221B2 (en) 2016-05-19 2020-11-10 Innas Bv Hydraulic device, a method of manufacturing a hydraulic device and a group of hydraulic devices
US10914172B2 (en) 2016-05-19 2021-02-09 Innas Bv Hydraulic device
US11067067B2 (en) 2016-05-19 2021-07-20 Innas Bv Hydraulic device

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NL2005504C2 (nl) * 2010-10-12 2012-04-16 Innas Bv Hydraulische inrichting met een spiegelplaat.
WO2012050446A1 (fr) * 2010-10-12 2012-04-19 Innas Bv Dispositif hydraulique comportant une plaque frontale
WO2012150069A1 (fr) * 2011-05-02 2012-11-08 Zf Friedrichshafen Ag Machine à pistons axiaux à axe incliné
EP3438451A4 (fr) * 2016-03-28 2019-10-30 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Machine rotative hydraulique
US10808686B2 (en) 2016-03-28 2020-10-20 Kobe Steel, Ltd. Hydraulic rotary machine
US10830221B2 (en) 2016-05-19 2020-11-10 Innas Bv Hydraulic device, a method of manufacturing a hydraulic device and a group of hydraulic devices
US10914172B2 (en) 2016-05-19 2021-02-09 Innas Bv Hydraulic device
US11067067B2 (en) 2016-05-19 2021-07-20 Innas Bv Hydraulic device

Also Published As

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KR20090020549A (ko) 2009-02-26
JP2009529619A (ja) 2009-08-20
WO2007104257A1 (fr) 2007-09-20
US20090007773A1 (en) 2009-01-08
CN101415944A (zh) 2009-04-22

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