AXIAL PISTON PUMP

Abstract: Axial piston pump comprising a rotatable cylinder block (16) within which at least one piston (20) is mounted slidable in a cylinder (18) and by rotation of the cylinder block is imparted a reciprocating movement by becoming inclined from a neutral or null position in which no pumping is effected, relatively a drive plate (14) in at least on direction. A distribution plate (22) adjustable jointly with the cylinder block (16) is formed with outlet and inlet slots (24, 26) which by the inclination adjustment are caused to communicate with exhaust and intake ports (A, B) for the outflow and the reflux, respectively, of the pumped medium, which ports are formed in a stationary port plate (28). The porte plate (28) has, in addition, at least one feed opening (32) for supply of pressure fluid to the pump. The exhaust and intake ports (A, B) and the feed opening (32) are so positioned in the stationary port plate (28) that the outlet and inlet slots (24, 26) of the distribution plate as a consequence of increased inclination of the distribution plate from null position are brought to gradually increasing communication with the feed opening (32) and the exhaust port (A or B) for the outflow from the pump, while the intake port (B or A) for the reflux to the pump simultaneously are opened gradually by the distribution plate (22). The intake port is connected to the pressure fluid supply to the pump.

Description: AXIAL PISTON PUMP The present invention relates to an axial piston pump comprising a rotatable cylinder block within which at least one piston is mounted sl idable in a cylinder and by rotation of the cylinder block is imparted a reciprocating movement, the cylinder by the rotation being brought to gradually changing communication with outlet and inlet openings in a valve or distribution plate which openings in turn are connected with exhaust and intake passages for the pumped edium. In known hydraul ic systems, especially for mobile units, ever increasing numbers of pump circuits are utilized to obtain independent functional operations under simultane¬ ous running, i .e. one hydraulic pump together with associat¬ ed circuit is used for each single operation, and all hydraulic pumps are driven by one driving motor. As the pumps which are used have constant displacement this arrange¬ ment implies that the entire pump volume must be circulated by pumping which means that the entire volume is caused to circulate even if no operation is desired to be effected in the circuit. Recently, systems have become available which are operated without complete reflux, which means that 20- 30 % only of the total volume is delivered via filter to a receptacle while the remainder of the volume is circulated by pumping in a separate circuit. Even if thus some improve- ment is attained with such a system, there still exists the great drawback that the circulation by pumping of the fluid, such as the hydraulic oil , requires a substantial portion of the driving motor effect for a circuit also which is not used for any operation. Additional drawbacks inherent to such systems are that tubing for circulation by pumping of the hydraulic fluid and the installation of a directional valve for control of the fluid flow increase the initial costs and compl icate the construction. As speed requirement (great volume) does not exist simultaneously with power demand (high pressure) , it is necessary, when a great power is being developed, to take charge of, and drain o-ff, a great fluid volume, when a minor volume only is utilized for the generation of power. One main object of the present invention is to pro¬ vide a new type of axial piston pump preferably for hydrau¬ lic systems in which e v e ry circulation by pumping of the hydraulic fluid can be eliminated, while the same readiness for operation as with known systems is retained. Another important object of the invention is to provide a pump of said kind the fluid volume of which can be regulated in response to load of, and output from, the pump in order to eliminate the disadvantageous effects described above. Further objects and advantages and the characteristic features of the axial piston pump according to the inven¬ tion will become apparent from the following description, considered in connection with the accompanying drawings which illustrate some preferred embodiments and form part of t is specification and of which:- Figure l* is a diagrammatic, partly sectional side view of an axial piston pump according to the invention forming part of a circuit for control of a cylinder. Figure 2 is a diagrammatic view from below of a valve or distribution plate of the pump in relation to the port plate of the pump housing, generally along line 11 -11 of Fi gure 1. Figures 3 and 4 are views corresponding to that of Figure 2 but with the distribution plate -in other positions. Figure 5 is a diagrammatic, partly sectional side view of a servo mechanism for control of the pump according to the invention. Figures 6 and 7 show another embodiment represented in similar manner as the preceding embodiment. The pump shown in Figure 1 comprises a housing 10 represented di agrammati cal ly and enclosing a rotatably mounted drive shaft 12 with drive shaft flange 14, which drive shaft is actuated by a drive motor not shown here. OM Pivotably mounted in the housing is a cylinder barrel or block 16 containing at least one cylinder 18. within which a piston 20 is received for reciprocating movement. The pistons 20 are mounted in usual manner in the drive shaft flange 14 e.g. by means of ball-formed bearings so that the cylinder block rotates with the drive shaft flange. The cylinder block 16 can be tilted relatively to the drive shaft flange 14 whereby the pistons on rotation of the cylinder block 16 are imparted a reciprocating movement Q within the cylinders, the stroke of which movement becomes dependent on the angle between the drive shaft 12 and the cylinder block 16. Disposed overhead of % the cylinder block is a valve or distribution plate 22 which is formed with slots 24, 26 (Figures 2-4), the pistons moving in outward 5 di ection through one of the slots 24, 26 becoming connected with an intake or suction port in the housing and the pis¬ tons which are on their way into the bores through the other slot 24,26 being in communication with an exhaust or pressure port in the pump housing 10. The exhaust or Q pressure port and the intake or suction port are denoted A and B, respectively, in the figures. The described pump according to the invention has variable o r adjustable dis¬ placement, i.e. the angle between the dr ve shaft flange and the cylinder block can be varied to an inclination from 0 5 to about 25 degrees in both directions from the neutral position shown in Figure 1 where the angle is 0. The angle is thus varied in the shown embodiment by a tilting displace¬ ment of the cylinder block 16 and the distribution plate 22 to the left or the right in the shown figure about the pivot 0 point x. The distribution plate 22 is rotationally stationary and thus does not participate in the rotation of the cylinder bl ock 16. According to the invention, there is pos tioned out¬ side the distribution plate 22 a stationary port plate 28 5 in which the intake and exhaust ports A and B, respectively, are provided. The port plate 28 is f-ixed to the pump housing and thus does not participate in the angular setting of the cylinder block 16 and the distribution plate 22. From OMPI_ IPO ■ Figure 2 there is evident the positioning of the ports when the distribution plate 22 is in the neutral position of the pump with the angle 0, i.e. the position shown in Figure 1. The sector surface of the housing 10 at the top portion of the pump is surrounded by a flange 30 by which the port plate 28 is rigidly secured to the pump housing. The distri bution plate 22 which extends to tight abutment against the sector surface of the housing 10 contains, as described earlier, the valve slots 24,26, and about these valve slots the sector surface of the cylinder block 16 is indicated in the form of a ring. Further, there are shown di agrammati cal ly port openings 32 for feed oil to the cylinder block 16 and the ports A and B, of which in the following descriptio the port A will be denoted intake port and the port B exhaus port. Of course, the relation of the ports to one another will be reversed when the direction of rotation is changed, which means that the port B will become the int-ake port and the port A the exhaust port. It will be easily understood from Figure 2 that no fluid, such as oil , in the neutral, po sition is supplied to the ports A, B from the cyl i nders 18 in the cylinder block 16. However, the distribution plate 2 leaves both in the port A and in the port B a gap 34, the function of which will be described nearer hereinafter. Fro said Figure 2 it will be evident also that the feed ports 32 are extended nearer to the centre line of the cylinder block 16 and the valve slots 24,26 than the ports A and B in order not to obtain too small an open area of the feed port 32 when the pumping operation is started, since other¬ wise cavitation could be caused. When the pumping operation is started, as is illustrated in Figure 3, fluid is sucked in from the feed opening 32 in the valve slot 26 through th portion 32a of the feed opening 32 then coinciding with sai slot 26 as the result of the pistons in the cylinders when passing below the valve slot 26 in the valve block 16 per¬ forming an inward movement in the cylinders 18 and sucking the fluid inwards from the port opening 32. By continued rotation of the cylinder block 16 the cylinders 18 filled with fluid when passing over the valve slot 24 will pump ou the fluid through the portion B ' laid open of the exhaust port B into duct 40 in Figure 1. The reflux from the operat¬ ing circuit streams through duct 42 back to the portion A 1 of port A laid open alongside the distribution plate 22 (Figure 3) . Figure 4 shows the corresponding position with the highest volume to the exhaust port B, i.e. when the cylinder block 16 has been tilted to the right as far as possible in Figure 1 , usually by about 25 relative the centre line of the drive shaft flange 14. As is evident from Figure 4, the feed opening 32 now coincides with the valve slot 26 and the exhaust port B with the valve slot 24 in usual manner. The enti e intake port A is laid open along- side the distribution plate 22. The shown and described axial shaft pump forms part of a system presented di agrammati cal ly in Figure 1 and including a control cylinder 36 with piston 38. In the shown embodiment the pressure fluid from the pump is fed through the pipe 40 from the pump 10 to the cylinder 36 and is re¬ turned through the p pe 42 from the opposite part of the cylinder. Inserted into each circuit or duct 40, 42 are non¬ return valves 44 and overflow valves 46 which through pipes 48 are coupled to the reverse circuit to or from, respective¬ ly, the cylinder 36. In the shown embodiment, there are also provided a pre-feed pipe 50 with non-return valve 52 and further a return pipe 54 from the pump to a receptacle 56, said pipe 54 containing a throttle valve 58 and an overflow valve 60 with bypass-pipe 62 and filter 63. The pre-feeding may be effected by means of, for example, a separate pump 64 from the receptacle 56. By the shown arrangement many advantages are obtained with the pump according to the invention when compared with known pumps, as will become evident from the following description: In the neutral position of the pump shown in the Figures 1 and 2, no circulation by pumping of the pressure fluid takes place. Therefore, no directional valve is required to direct the flow between the intake and exhaust ducts 40, 42 and also drainage to receptacle is dropped. The feed pressure from the pre-feeding (the pipe OMPI IPO ^ 50) of 1.5 MPa, for example, acts through the slots 34 in the ports A and B on the one or the other side, respective¬ ly, of the cylinder. Since the pump is set in the angle 0, negligible power only is required to drive the pump in i this position, for which reason no slipping clutch device for the pump need be provided. Slipping clutch devices are found in known pumps which devices require power even when no fluid is taken out to any operational circuit because of . the circulation by pumping of the fluid. When pumping is 10 started in the pump according to the invention which is show in Figure 3, the cyl inder block 16 and the distribution plate 22 are tilted so much only as the- operation requires, which means that when an operation with little volume is desired, it is possible also with constant number of revo- 15 lutions of the driving motor to achieve much softer starts, and the operations can be run for a long time at low speed without any negative temperature effects. This should be compared with the pumps described at the outset above where full volume always is present and, therefore, a great flow 20 must be blocked in order to obtain a high pressure while at the same time the major part of the fluid is carried off without being utilized, which results in heavy heat genera¬ tion. When the pressure is increased, the pump is positive- 25 l guided to a minor angle against the deflecting power in . almost the same manner as a piston pump with variable dis¬ placement, but the positive guiding continues towards the angle of zero which implies that overflow oil need not aris Therefore, the power requirement can be less than when pump 30 with variable di spl acemen-t are used. The positive guiding may be effected by means of, for example, the servo mecha¬ nism shown in Figure 5 for controlling and centering the tilting of the pump. Hydraulic fluid is supplied to servo cylinder 70 with servo piston 72 through, for example, pipe 35 74 and a servo control device 76. The servo fluid may be, for example, a branch portion of the pre-feed flu d (the pipe 50) to the pump in Figure 1. When the servo valve is opened for pressure via pipe 78 to the rear side of the O " piston 72, this piston 72 over its piston rod 80 acts on the distribution plate 22 coupled to the piston rod 80 to¬ gether with the cylinder block 16. Thereby, the outward incl nation of the pump is increased and pumping to the port A is started. Via bores 82, " 84 leading to the ports or openings A and B, respectively, this piston 86 between centering sp ings 88, 90 scans the working pressure of the pump. When the working pressure rises, the piston rod 80 is displaced against the pressure in the servo cyl nder 70, i.e. the control power, by the higher pressure acting on the piston 86. When the pressure reaches the desi ed high¬ est value, the pump is returned so that the pumping is dis¬ continued even if the servo pressure is still active in the pipe 78. The same holds true when the pressure fluid instead is supplied to the servo pipe on the front side of the piston, viz. through pipe 92. To compensate for the differ¬ ent piston areas of the servo piston 72, the piston 86 also may have different piston areas on its one and other side (not shown). In the embodiment of Figure 1 , the ports A and B are exhaust or intake ports, depending on in what direction the cylinder block 16 and the distr bution member 22 are in¬ clined. To compensate for the different piston areas of the piston 38 because of the existence of the piston rod 39, the inclination movement in the one direction, for example towards the right in Figure 1 , may be limited by means of a mechanical stopper (not shown) so as to obtain a lower maximum volume for the pump flow to the front side (with the piston rod 39) of the piston 38 which side has the smallest area. In this way the sane speed is obtained for both directions of movement of the cylinder 36. The non¬ return valves 44 and overflow valves 46 in each pipe 40,42 are preferably devised as sleeve type valves so that over¬ flow of fluid from one side to the other results in slow opening of the non-return valve so as to prevent sudden pressure drop to occur in the reflux fluid. The pre-feed pressure is no absolute necessity in the system, but it renders many advantages in a system having a plurality of operative functions. As described, it can be * used through the servo control device 76 to select directio and speed, in which connection also a v e ry small risk of ca vitation exists. Oil exchange , and filtering are effected, as described, via throttle valve 58 and-pressure limiting valve 60 and filter 63 to receptacle 56. For the hydraulic balancing of the distribution plate 1 2 it may be suitable to position the exhaust parts as is evident from Figs. 6 and 7 in order to try to get the hydra " lie balance against the opposite surface. Fig. 6 shows a view similar to Figure 1 of a modified embodiment and Figur 7 shows a section along line V11-V11 in Figure 6, the same reference numerals being employed as before under addition of the number one hundred. The exhausts A" and B" may here open on both sides of the distribution plate 122. The passage of each port to the associated intake duct 132 is realized as before. To equalize the pressure which in axial direction acts against the bearing, the port in this posi¬ tion becomes closed against the sector surface, and balance can be reached. As becomes evident from the preceding description, the drawbacks which generally are inherent to all known systems with directional valves, viz.: 1. interference between loads within the same pumping circuit, 2. no direct interaction between deflection of the control rod and speed, 3. great losses which, in addition, must be cooled off, will be eliminated in the system according to the invention For item 1 this is achieved by means of separate pumping circuits to the operative functions when simultane¬ ous running is required. Regarding item 2 the system according to the inventio affords the possibility of direct reciprocity between de- flection of the control rod and the speed of the operative function irrespective of the magnitude of the load. O PI The losses according to item 3 can be reduced consider¬ ably in the present system depending on the factors which are set forth in the description of the functional opera¬ tions. As is evident from the aforesaid, it is essential for the correct operation of the pump that the port plate comprises at least one feed opening for supply of pressure fluid to the pump and that the arrangement of the exhaust and intake channels and the intake port in the stationary port plate is of such a kind that the outlet and inlet slots or apertures by outward inclination of the distribution plate from zero position are brought to gradually increasing communication with the feed opening and the exhaust channel (A or B) for the discharge of fluid from the pump, the in¬ take channel (B or A) for the reflux to the pump becoming opened gradually simultaneously by the distribution plate, which intake channel is connected to the pressure fluid feed to the pump, more distincly the pump housing 10, which serves as reservoir for the pressure fluid. In this way. the volume difference between the two faces of the piston 38 of the pressure fluid cylinder 36 is prevented from in¬ fluencing the operative function. -i ϊ Ttr OMPI > & °\*

Claims: CLA I MS 1. An axial piston pump comprising a rotatable cylinder block (16) within which at least one piston (20) is mounted slidable in a cylinder (18) and on rotation of the cylinder block is imparted a reciprocating movement by becoming tilted from a neutral or null position in which no pumping is effected, relatively to a drive plate (14) in at least one direction, and a distribution plate (22) adjustable jointly with the cylinder block (16) and formed with outlet and inlet slots (24,26) which by the adjustment are brought to communication with exhaust and intake ports (A,B) for the outflow and the reflux, respectively, of the pumped medium, said ports being formed in a stationary port plate (28), c h a r a c t e r i z e d in that the port plate (28 in addition, comprises at least one feed opening (32) for supply of pressure fluid to the pump and that the disposal of the exhaust and intake ports (A,B) and the feed opening (32) in the stationary port plate (28) is of such kind that the outlet and inlet slots (24,-26) of the distribution plat in consequence of the tilting of the distribution plate fro neutral position are brought to gradually increasing commu¬ nication with the feed opening (32) and the exhaust port (A or B) for the outflow from the pump, the intake port (B or for the reflux to the pump simultaneously being opened gradually by the distribution plate (22) which intake port is connected to the pressure fluid supply to the pump. 2. The pump according to claim 1 , c h a r a c t e r ¬ i z e d in that the pressure fluid supply to the pump consists of a receptacle to which both the feed opening (32) and the intake port (A or B) are connected. 3. The pump according to claim 2, c h a r a c t e r i z e d in that said receptacle is constituted by the pump housing (10). O P IP 4. The pump according to any of the claims 1 - 3, c h a r a c t e r i z e d in that a gap (34) remains open in both the intake and the exhaust ports (A.B) when the distr bution plate (22) is in the neutral position, 5 " said gap permitting influx and outflow of pressure fluid into, and out of, the pump housing (10) . 5. The pump according to any of the claims 1 - 4 having the cylinder block (16) and the distribution plate 10 (22) settable in two directions from the neutral position for two different pumping directions, c h a r a c t e r - i z e d in that the setting in at lea^t one direction is made variable by means of a mechanical stop. 15 6. The pump according to any of the claims 1 - 5, c h a r a c t e r i z e d in that the feed opening (32) for supply of pressure fluid to the cylinder or cylinders (18) is opened prior than the exhaust port (A or B) of the pump when the angle of inclination is increased from the 20 -null posi tion . 7. The pump according to any of the claims 1 - 6, c h a r a c t e r i z e d in that the pump forms part of a pre-feed circuit (50) for maintenance of a pre-feed 25 pressure in the pumping circuit. 8. The pump according to any of the claims 1 - 7, c h a r a c t e r i z e d in that the outward tilting or adjustment of the cylinder block (16) and the distribution 30 plate (22) is effected by means of a servo mechanism within which a servo piston (72) coupled to the cylinder block or the distribution plate is actuated by a control circuit (78,92) via a servo regulator (76), the servo piston (72) also being actuated by the working pressure of the pump in 35 such a manner that the servo piston (72) s displaced against the servo control pressure when this pressure is exceeded by the working pressure. 9. The pump according to claim 8, c h a r a c t e r - i z e d in that the intake and exhaust ports (A, B) of the pump are connected to one and the other side, respec¬ tively, of a piston (86) provided on the piston rod (80) of the servo piston (72). 10. The pump according to claims 7 and 8, or 9, c h a r a c t e i z e d in that the pre-feed pressure (50) is used as servo control pressure. OMP WIP

Inventors: GRELSSON B
Applicants: GRELSSON B
Application year: 1980
Main classification: F04B1
IPC codes: F04B1