Axial plunger pump with integrated axial piston energy recovery device

Abstract

An axial piston pump with an energy recovery system.

Description

[0001] Related applications

[0002] Pursuant to 35 USC 111(b), this application claims priority to U.S. Provisional Application No. 63 / 524,722, filed July 3, 2023, the disclosure of which is incorporated herein by reference in its entirety. Background of the Invention

[0003] Many industrial fluid-based processes involve process flows that need to be pressurized to the high levels required for beneficial process flow transformation. The flow entering the process is called the input flow. The output of the process can be a single output flow or multiple output flows, where one or more of the output flows retain most of the input pressure. High-pressure output flows can potentially recover hydraulic energy to reduce net energy consumption.

[0004] Figure 1-A A reverse osmosis desalination system is depicted. The input stream (seawater in this example) enters through pipe 1 and is pressurized to approximately 55 to 65 bar by a high-pressure pump 2 before passing through the reverse osmosis (RO) membrane 3. The RO membrane 3 selectively prevents dissolved substances from crossing the semi-permeable membrane of the RO element, and thus a portion of the input stream is purified and exits at low pressure through pipe 4. At any given time, 35-50% of the input stream is purified, and 50-65% of the input stream exits the membrane 3 as an output brine stream at a slightly lower pressure than the input stream in pipe 1, passing through pipe 5 and control valve 6 to drain port 7. This output brine stream provides the potential for recovering hydraulic energy. Figure 1-B An energy recovery device 8 is shown, which transfers energy from the output flow in pipe 5 to the input flow in pipe 1. Note that the input flow has a significantly higher flow rate than the output flow.

[0005] Figure 1-C A liquid-based absorption process for purifying gases such as natural gas is described. The feed gas enters a pressurizer 52 via pipe 1. A liquid absorbent is injected from a nozzle 53 located at the top of the pressurizer, absorbing CO2 from the upward-flowing gas. The purified gas exits via pipe 54. The absorbent, now carrying contaminants, is collected at the bottom and exits via pipe 58 through a control valve 57 regulated by a level monitor 56. The absorbent output flows into a stripper 59, which removes contaminants from the liquid absorbent. The contaminants exit via pipe 60 and then through pipe 61 to a pump 55, which repressurizes the absorbent to the pressure in the pressurizer 52, thus completing the purification cycle. A typical pressurizer pressure is 60 bar, while the stripper pressure is much lower than 10 bar, thus allowing significant hydraulic energy to be recovered. Figure 1-D An energy recovery device 8 is shown, which transfers hydraulic energy from an output flow through pipe 58 to an input flow through pipe 61. Note that the input and output flows have similar flow rates.

[0006] The process described above has an input flow rate approximately equal to the output flow rate. Furthermore, the output flow carries gaseous components, which precipitate from the solution when the pressure decreases. Therefore, the output flow volume can exceed the input flow volume and contains additional energy generated from the expansion of the gaseous components.

[0007] The present invention described herein can be adapted to the above-mentioned operating scenarios.

[0008] Many types of hydraulic energy recovery devices have been developed. Most use turbines to recover hydraulic energy. The mechanical energy generated by the turbine can be used to help drive a booster pump or for another application. Turbine-based energy recovery is suitable for high flow rates (above 100 m³ / s). 3 / hr is the most feasible, which is beneficial for high efficiency. Lower flow rates negatively impact efficiency, thus reducing the economic viability of using such equipment. Positive displacement energy recovery equipment can achieve high efficiency at low flow rates, but is generally more expensive, thus reducing its economic viability.

[0009] This invention improves process hydraulic energy recovery by combining a pressure pump and a pressure-reducing energy recovery device into a single unit with positive displacement. Combining the high-pressure pump and energy recovery device into one unit reduces system cost and complexity, thus making energy recovery more economically viable for various processes. The added flexibility in handling input and output streams with varying flow rates and gaseous components increases the scope of application and energy recovery potential.

[0010] Description of the prior art

[0011] Figure 2 and Figure 3 A typical axial piston pump related to the present invention is shown. The housing 75 and end caps 72 and 21 are attached by bolts 74-A and 74-B and bolts 22-A and 22-B, respectively. A shaft 24 with a keyway 25 passes through the end cap 21, where a seal 31 prevents leakage. The inner end of the shaft 24 is attached to the cylinder 12 by a keyway 26 and a key 27, thus rotating as a single unit.

[0012] The swivel plate 20 is attached to the end cap 21 by bolts 23-A and 23-B. The swivel plate 20 is cylindrical and is cut or set at an angle of approximately 15 to 25 degrees relative to the end cap 21. Figure 3 As illustrated more clearly, cylinder 12 (in bold outline for clarity) comprises a plurality of axially arranged cylinders 11 circumferentially arranged around the centerline of cylinder 12. The number of cylinders is typically 5, 7, or 9, with higher numbers providing smoother fluid flow and lower numbers reducing manufacturing costs. Port plates 77 are held to end caps 72 by bolts 74A and 74B.

[0013] Piston 10 in each cylinder 11 is connected to connecting rod 38, and connecting rod is attached to spherical ball 32. Ball 32 engages in socket 13 with an engagement sufficient to limit the ball 32. Socket 13 and ball 32 are freely pivotable relative to each other. Socket 13 is attached to slide 14. Slide 14 slides freely across a rotating ramp in a circular path defined by the position of cylinder 11 in cylinder 12. Lubrication passage 18 connects pumping chamber 19 to bearing recess 17 in slide 14. Fluid pressure in chamber 19 is transmitted to bearing recess 17 to provide hydrostatic lift, thereby creating operating clearance 15, which reduces friction and wear between slide 14 and rotating ramp 20 during operation.

[0014] In operation, shaft 24 and cylinder 12 are rotated by a motor, as is known in the art. As cylinder 12 rotates, slide 14, connecting rod 38, and piston 10 reciprocate as slide 14 conforms to the angled rotating ramp 20. This reciprocating motion is timed, such that as piston 10 moves away from port plate 77, cylinder 10... Figure 3 The suction inlet 1 and the suction arc-shaped region 36 of the port plate 77 shown in the figure are connected. The input fluid is drawn into the cylinder 11 through the inlet connection 1. At a point during the rotation of the cylinder 12, the reciprocating motion slows down, then stops, and then begins to reverse towards the port plate 77. During the transition between the suction and discharge strokes, the cylinder 11 is covered by the tight-fitting operating seal regions 35 and 37 of the port plate 77, as shown in the figure. Figure 3 The optimal diagram is shown below. Crucially, the width of the convex regions 35 and 37 between ports 34 and 36 must be wider than the diameter of cylinder 11; otherwise, leakage would occur between ports 34 and 36. This tight operating clearance minimizes leakage from the high-pressure port 34 to the low-pressure port 36. Further rotation of cylinder 12 causes piston 10 to move toward port plate 77. Cylinder 11 is now in communication with the arcuate high-pressure port 34 of port plate 77, which in turn communicates with output port 2. As piston 10 moves toward port plate 77, the reduction in volume of cylinder 11 caused by the forward movement of piston 10 results in a pressure increase in cylinder 11 to the pressure present in discharge outlet 2 and downstream piping. The preceding description is a typical description of an axial piston pump.

[0015] In the discharge arc (pumping section), the pressure between the port plate 77 and the cylinder 12 will be high, tending to force the cylinder away from the port plate. This force can be counteracted by constricting the neck of the opening in the cylinder 11 (as indicated by shoulder 28). Fluid pressure will act on the area of ​​shoulder 28, pushing the cylinder toward the port plate 77. By using the correct area of ​​shoulder 28, the pressure from the port plate 77 can be largely balanced with the small net force required to maintain a near-grip gap, thus reducing leakage from the high-pressure area to the low-pressure area.

[0016] Bearing 8 maintains the radial position of sleeve 12. Small clearance 9 allows for lubrication and cooling flow.

[0017] Leakage from cylinder 12, piston 10 and bearing recess 17 is discharged through discharge port 30.

[0018] Figure 4 Other prior art is shown, depicting an axial piston pump with hydraulic energy recovery functionality. Pump section 80 is similar to... Figure 2 The pump. A key feature here is the second port plate 68 located at the opposite end of cylinder 12. The high-pressure brine output flow, such as the output flow exiting the RO membrane 3 through pipe 5 as shown in Figures 1A and 1B, enters through inlet port 69, flows through port plate 68, and enters energy recovery cylinder 81. The fluid pressure acting on the bottom 76 of the piston generates a force that reduces the energy required to achieve the discharge pressure and reduces the load on the rotating ramp 73. The force reduction is equal to the cross-sectional area of ​​piston 66 minus the cross-sectional area of ​​connecting rod 67 multiplied by the pressure of the output flow. This force acting on the bottom 76 of piston 66 multiplied by the piston stroke is equal to the amount of energy recovered by the cylinder minus frictional losses.

[0019] During the suction stroke, the fluid acting on the top of the piston 65 in the pump cylinder 11 causes the piston to move toward the rotating swashplate 73. The fluid movement in the energy recovery cylinder is discharged through the port plate 68 and the flow passage 70.

[0020] The connecting rod 67 reduces the volume of displacement swept by the reciprocating motion of pistons 65 and 66, therefore the output flow rate needs to be smaller than the input flow rate. In the case of a reverse osmosis system, the output brine flow is typically 50% to 65% of the input volume of the process flow, so the rod cross-sectional area should be similar in size to the input and output flow volumes.

[0021] Figure 4 The obvious problems with the prior art described herein include the gaps between the cylinder 12 and the port plates 77 and 68. It is impossible to ensure that both gaps are simultaneously tight or only slightly abrasive. Attempts to manufacture parts to achieve micron-level gaps, even if possible, cannot accommodate dimensional changes caused by wear, thermal growth, or pressure.

[0022] It should also be noted that the diameter of cylinder 12 is significantly increased to accommodate flow channels 69 and 70, resulting in increased cost and greater leakage around the cylinder. Summary of the Invention

[0023] An axial piston pump with an energy recovery system. Attached Figure Description

[0024] Figure 1A is a side elevation view of the reverse osmosis desalination system.

[0025] Figure 1B is a side elevation view of a reverse osmosis desalination system with energy recovery equipment.

[0026] Figure 1C is a side elevation view of the liquid-based absorption process.

[0027] Figure 1D is a side elevation view of a liquid-based absorption process with an energy recovery device.

[0028] Figure 2 This is a cross-sectional side view of an axial piston pump.

[0029] Figure 3 It is along Figure 2 The cross-sectional view of the plane cut by the wire cutting plane AA.

[0030] Figure 4 This is a cross-sectional side elevation view of an axial piston pump with existing technology for energy recovery.

[0031] Figure 5 This is a cross-sectional side elevation view of the axial piston pump of the energy recovery device of the present invention.

[0032] Figure 6 It is along Figure 5 The cross-sectional view taken by the cutting plane line BB in the diagram.

[0033] Figure 7 This is a cross-sectional side elevation view of another embodiment of the axial piston pump of the energy recovery device of the present invention.

[0034] Figure 8 It is along Figure 7 The cross-sectional view taken by the cutting plane line CC in the diagram.

[0035] Figure 9 This is a side elevation view of another feature of the present invention.

[0036] Figure 10 This is a side elevation view of another feature of the present invention.

[0037] Figure 11 It is a cross-sectional view taken along line AA in Figure 1.

[0038] Figure 12 It is a cross-sectional view taken along line BB in Figure 1.

[0039] Figure 13 It is a cross-sectional view taken along line CC in Figure 1.

[0040] Figure 14 This is a side elevation view of another feature of the present invention. Detailed Implementation

[0041] Figure 5 and Figure 6 An embodiment of the invention combining an axial pump with an energy recovery function is depicted. Much of the pump portion is similar in construction and operation to that described above as prior art, and therefore will not be repeated here. However, similar components will be referenced in the following description. The invention will be described as an axial piston high-pressure pump 2 that supplies feed to a reverse osmosis membrane 3 under pressure, as depicted in Figures 1A and 1B. The energy recovery portion of the pump utilizes the high-pressure brine flowing from the membrane through pipe 5.

[0042] Many processes, such as RO desalination, involve input and output streams containing particulate matter. Figure 5 The filter 16 at the top surface of the piston 10 prevents particulate matter from passing through the lubrication channel 18 and entering the bearing recess 17, otherwise the particulate matter would have damaged the slide 14 and the rotating swashplate 20.

[0043] The energy recovery section 39 has a low-pressure outlet 43 and a high-pressure inlet 44. The high-pressure outlet is configured to receive the brine output flow from the RO membrane in pipe 5, as shown in Figures 1A and 1B. Outlet 43 and inlet 44 are in fluid communication with circumferential channels 46 and 45, respectively, and... Figure 6 This is better illustrated in the text.

[0044] Figure 5 and Figure 6 The energy recovery cylinder 79 leads to the high-pressure channel 45 and the low-pressure channel 46. A connecting rod 38 passes through the high-pressure and low-pressure channels and through the seal 40. Lands 48 and 49 are in close contact with the cylindrical sides of the cylinder 12, minimizing leakage between the high-pressure chamber 45 and the low-pressure chamber 46. The circumferential width of each land is greater than the circumferential width of the energy recovery cylinder port 41, thus minimizing leakage from the high-pressure channel 45 to the low-pressure channel 46. Flow arrows indicate the general direction of entry and exit from the cylinder.

[0045] During operation, the input fluid to be pumped enters through inlet pipe 61 and is discharged at high pressure through outlet 62 in response to the rotation of cylinder 12, which has a reciprocating piston 10 in cylinder 11. A rotating ramp 20 causes the piston 10 to reciprocate to provide pressurization as described in more detail previously.

[0046] As previously discussed, the high-pressure brine output from the RO membrane enters port 44 and flows into the circumferential channel 45. The piston 10 moves upward toward the port plate 77, allowing the high-pressure fluid to enter the energy recovery cylinder 79 through port 41 and act on the region 42 of the piston 10 adjacent to the connecting rod 38. Figure 5As shown in the diagram, the force acting on piston 10 is equal to the piston area 42 multiplied by the fluid pressure. This force reduces the net force required to drive piston 10 toward port plate 77. Therefore, the torque applied by shaft 24 to generate rotation of cylinder 12 relative to rotating ramp 20 and to reciprocate piston 10 is reduced, thereby reducing motor energy consumption.

[0047] As the given piston 10 moves toward the port plate 77 to the top dead center of its stroke, the rotation of the cylinder 12 causes the energy recovery port 41 to move across the convex region 48, which minimizes leakage from the high-pressure channel 45 to the low-pressure channel 46. Note that the piston's axial velocity is essentially zero at both the top and bottom dead centers. Due to the rotation of the cylinder 12, the energy recovery cylinder 79 and the piston 10 then enter the channel 46 and move downwards, discharging fluid from the energy recovery cylinder 79 through the energy recovery port 41 into the channel 46 and through the outlet 43.

[0048] The displacement of the piston stroke in the energy recovery section 39 is equal to the area of ​​cylinder 11 multiplied by the stroke length of piston 10. However, the force acting on region 42 of the connecting rod 38 reduces the piston area, thereby reducing the displacement. For example, a connecting rod with a diameter of 50% of the piston diameter means that the displacement on the energy recovery side of the piston is approximately 70% of that on the pumping side. For some processes such as reverse osmosis, the brine output flow is approximately 50% of the input flow, thus allowing for a feasible connecting rod diameter. If the output flow equals the input flow, the connecting rod diameter would need to be zero, which is obviously not feasible.

[0049] Figure 7 Another feature of the invention is illustrated, which allows the output flow rate to be equal to or greater than the input flow rate, and allows a sufficiently large connecting rod to reliably bear mechanical loads. This operating scenario would be used in typical gas processing, refining, ammonia, and petrochemical production processes, where the output flow rate is equal to or greater than the input flow rate. Piston 10 has an additional piston section 50 with a diameter larger than that of piston 10. Cylinder 11 has a larger diameter to accommodate piston section 50. The diameter of piston section 50 is set to be sufficient to increase displacement to handle the output flow rate, while also taking into account the diameter of the connecting rod 38 required to handle mechanical loads.

[0050] Operation as before Figure 5 and Figure 6The pump described herein is the same. However, the cylinder volume 83 formed in cylinder 11, defined by the first piston section surface 82 and the second cylinder section surface 89, changes due to the reciprocating motion of the piston 50. Therefore, cylinder volume 80 must be vented to allow fluid inflow and outflow. One method for venting is to include a passage 84 that connects the top of volume 80 to drive-end volume 85. Another method is to use a vent port 86 that connects volume 87 between cylinder 12 and housing 75 to a line 88 extending from volume 87 to drive-end volume 85. This allows piston leakage to be drained into volume 85 and drain port 30.

[0051] Another feature is the ability to accommodate output streams containing gaseous components, which are gases contained in the solution and released when the fluid is depressurized. In this case, it should be specified that the liquid / gas flow is allowed to undergo expansion to capture additional energy.

[0052] Figure 8 The diagram illustrates how to achieve cylinder 79 (e.g.) Figure 5 The necessary modifications are made for fluid expansion within the cylinder 79 (shown in the diagram). Convex regions 48 and 49 provide a seal between the high-pressure channel 45 and the low-pressure channel 46. To accommodate the expansion of the output flow in cylinder 79, the circumferential length of the convex region 48 extends in the direction opposite to the rotation of cylinder 12, as indicated by arrow 90. Therefore, the fluid entering the energy recovery cylinder 79 terminates before completing its full stroke. Once the cylinder is sealed off from the high-pressure channel 45, the volume of fluid containing dissolved gas within cylinder 79 expands freely until cylinder 79 reaches the low-pressure channel 46. The diameter of piston 50 is designed to account for the reduced time the piston spends communicating with the high-pressure channel 45 in order to receive the correct amount of output fluid. For example, if the circumferential length of the convex region 48 is increased by 15% for gas expansion purposes, the amount of time the cylinder 79 spends communicating with the high-pressure channel 45 will be reduced by a similar amount of 15%. This reduced communication time can be compensated for by increasing the diameter of cylinder 79. The amount of energy available for recovery is a function of the output flow volume and pressure. Output flow energy losses are associated with frictional losses through piping, fittings, and valves.

[0053] use Figure 7 and Figure 8As illustrated, a tight operating clearance is required to minimize leakage. Ceramic rings 91 and 92 are attached to the housing 75 above and below the circumferential channels 45 and 46, respectively. Oppositely arranged is ceramic ring 93 with a radial clearance of 0.025 mm or less, and ceramic rings 91 and 92 are attached to the cylinder 12. The cylinder 12 is encased in ceramic in the region having a tight rotational clearance with the protrusions 48 and 49. Protrusions 48 and 49 have ceramic surfaces 96 and 97, which are tightly closed with the cylinder 12. The surface of the cylinder 12 opposite to the port plate 77 can also be ceramic-coated. Furthermore, the port plate can be made of ceramic material. Ceramic is the preferred material; however, various combinations of other non-abrasive and dimensionally stable materials can also be used.

[0054] like Figure 9 As shown, another operating scenario for the axial piston pump 104 (details of which have been described previously) is driven solely by a high-pressure fluid flow, thus eliminating the need for a motor or other actuators that might be required in hazardous areas such as those containing flammable gases. In this embodiment, the input fluid enters through the inlet connection 106 and exits through the outlet connection 107. The high-pressure pump 101 is driven by an electric motor 102 or other prime mover. The high-pressure fluid from the discharge connection 103 communicates with the high-pressure inlet 44 of the axial piston pump 104. The cylinder / piston diameter of the energy recovery section 39 is determined by the flow rate and discharge pressure of the motor-driven pump 101 and the desired flow rate and pressure difference at the pump end outlet 62 of the pump 104 of the present invention. For example, the discharge pressure at the pump end outlet 62 can be twice the pressure of the inlet pressure of the energy recovery section 39, so the working diameter of the energy recovery piston will be the pump piston area plus the area occupied by the connecting rod (e.g., Figure 5 It is approximately 1.41 times that shown in the figure. Figure 9 The embodiment shown has a closed hydraulic circuit arrangement utilizing connecting pipe 105, in which the low-pressure output flow exiting through the outlet connection 43 of the energy recovery section 39 is recirculated back to the inlet connection 100 of the motor-driven pump 101. This arrangement maintains the purity and other physical and chemical properties of the recirculated flow and the process fluid pumped by the axial piston pump 104.

[0055] refer to Figure 10The axial piston pump / energy recovery device (APP / ERD) system 200 has an end cap 201 attached to a housing 204 by bolts 202, wherein an O-ring 203 provides a seal. A fluid inlet port 205 allows fluid to enter the housing 204, and a fluid outlet port 220 discharges fluid from the housing 204. A cylinder 211 is driven by rotation of a shaft 210, which is secured to the cylinder 211 by a key 209. Pump cylinders 227 are evenly arranged in the cylinder 213. Each cylinder contains a piston 216, which includes a lubrication passage 215 and a fluid filter 217. ERD inlet 9 and ERD outlet 8, as well as piston seal 12, have been previously described. The housing 204 includes a bearing recess 222 adjacent to the cylinder 211. A flow passage 221 extends from the pump discharge port 220 to the bearing recess 222, wherein the passage includes a grooved channel in the face of the housing 204. The needle valve 224 can be adjusted to control the flow resistance through the channel 221. The bearing 213 has a recess 218 on the discharge side and a recess 207 on the inlet side, which are spaced 180 degrees apart.

[0056] refer to Figure 11 The bearing 213 surrounds the cylindrical portion of the cylinder 211 with a tight clearance 206 relative to the cylinder 211. The bearing region of the hydrostatic bearing recess 222 is biased toward the high-pressure side of the cylinder 211 to accommodate the greater thrust generated by the high cylinder pressure in this region.

[0057] refer to Figure 12 The number of pistons in the cylinder is typically 5, 7, or 9. Circumferential passage 230A connects each pump cylinder to outlet port 220. Circumferential passage 230B connects each pump cylinder 227 to inlet port 205. Bearing sections 228 and 229 of bearing 213 span the passages to connect the bearings and serve as a tight operating pressure seal between inlet port 205 and outlet port 220.

[0058] refer to Figure 13 The second circumferential bearing recess 207 will have a larger circumferential length than the first circumferential bearing recess 218. A groove 214 in the inner diameter of the bearing 213 connects the first circumferential bearing recess 207 and the second circumferential bearing recess 218. The groove 214 transmits high-pressure pumping from the first circumferential bearing recess 218 to the second circumferential bearing recess 207.

[0059] During operation, due to the rotation of cylinder 211, piston 216 within cylinder 211 experiences a reciprocating motion imparted by rotating swashplate 226, generating a suction effect and a pressure rise effect as previously described during its movement toward the rotating swashplate. The high pressure at pump outlet 220 and ERD inlet 209 combines to generate a strong force pushing cylinder 211 perpendicular to the axis of rotation in the direction of pump inlet 205. To counteract this force, a second circumferential bearing recess 207 is supplied with high-pressure fluid from the first circumferential recess 218 via groove 214. The high pressure in the second circumferential recess 207 acts as a hydrostatic bearing and prevents rubbing contact between cylinder 211 and bearing 213.

[0060] The pressure in block 219 of the ERD region of cylinder 211 and the high pressure during the pump stroke of piston 227 generate a force toward end cap 203. This force is counteracted by high-pressure fluid in bearing recess 222 provided by passage 221 connected to pump outlet 220. Needle valve 224 can be adjusted as needed to ensure sufficient pressure to prevent rubbing contact between cylinder 211 and bearing 213, without allowing excessive flow that could reduce efficiency or create unstable positions in cylinder 211.

[0061] like Figure 14As shown, the previously described axial piston pump can be modified for use as a curved-axis axial piston pump. In this arrangement, pump 316 has a drive shaft 118 with a keyway 333. Bearings 327 and 329 accommodate radial and axial forces on drive shaft 118. Seal 325 prevents leakage in bearing cavity 337. Drive shaft 118 is attached to drive plate 315 and is angled relative to pump shaft 317. Pump shaft 317 is driven by gear 319 attached to pump shaft 317, which engages gear 321 attached to drive plate 315. Piston 216 in cylinder 130 in cylinder 128 is attached to piston rod 219, which is attached to ball 305 enclosed by bearing socket 307. Note that piston 216 and piston rod 219 move in a reciprocating linear motion within cylinder 130. A socket 307 is attached to a rod 309, which is attached to a ball 311. The ball 311 is closed by a socket 313 attached to a drive plate 315. Rotation of the drive plate 315 causes the cylinder 128 and cylinder 130, as well as the piston 216 and piston rod 219, to move in a circular motion. However, due to the misalignment of the drive plate 315 relative to the pump shaft 317 and the attached cylinder 128, the socket 313, ball 311, and shaft 309 move in an elliptical motion relative to the piston rod 219. Therefore, the movable joint formed by the ball 305 and the socket 307 allows for changes in angle during rotation. Note that the invention requires the piston rod 219 to remain aligned with the cylinder 130 to allow the seal 211 around the piston rod 219 to function properly. Additional ball 305 and socket 307 connections are necessary to accommodate the requirements of the seal 211. The pump cylinder 128 has several cylinders 130, typically 5, 7, or 9. The cylinder and piston are positioned at an angle to the drive plate, typically between 20 and 40 degrees. The rotating cylinder, drive plate, piston, inlet, and outlet connections are similar in design and operation to the rotating ramp variant of the invention as previously described.

[0062] Figure 15 and Figure 16 This illustrates another feature of the invention, which is similar to that previously described in Figure 7 The variable diameter piston described herein. The function and configuration of piston 10 are related to... Figure 7 and Figure 8 The descriptions are the same, and for the sake of brevity, they will not be repeated, as these details have already been covered in previous articles. Figure 7 and Figure 8 The description covers this. Figure 15 and Figure 16 The pump also utilizes Figure 10 and Figure 11 The configuration includes a fluid inlet port 205 and a fluid outlet port 220 housed within a casing 204. Details of this arrangement are described in... Figure 10 and Figure 11The details are shown in the figures and will not be repeated for the sake of brevity, as the prior art can be referenced.

[0063] The detailed description above and in the accompanying drawings are intended to illustrate the features of the invention. It should be understood that the invention is intended to cover all modifications, equivalents, and alternatives within the scope of the following claims.

Claims

1. An axial piston pump, comprising: The shell has an inlet port and an outlet port; A rotatable cylinder having a plurality of cylinders positioned in a housing, the cylinders being configured to communicate with the inlet port and the outlet port when the cylinder rotates; A piston, movably positioned in each of a plurality of cylinders, having a first end and a second end, wherein the first end of the piston communicates with the inlet port and the outlet port when the cylinders rotate; Multiple connecting rods having a first end and a second end, the first end of the connecting rods being connected to one of the pistons, and the second end of the connecting rods being operatively engaged with an angled plate; A drive unit, operatively connected to the cylinder to rotate the cylinder, causes the piston to move in multiple cylinders as the second end of the connecting rod moves along the angled plate. A high-pressure inlet is formed in the housing. When the plurality of cylinders are in communication with the outlet port in the housing, the high-pressure inlet is in communication with the plurality of cylinders. The high-pressure inlet is configured to align with the connecting rod and the second end of the piston in the plurality of cylinders. as well as A low-pressure outlet is formed in the housing, and when the plurality of cylinders are in communication with the inlet port in the housing, the low-pressure outlet is in communication with the plurality of cylinders, and the low-pressure inlet is configured to align with the connecting rod and the second end of the piston in the plurality of cylinders.

2. The pump according to claim 1, wherein, The piston has a first section adjacent to the inlet port and a second section adjacent to the connecting rod for the piston.

3. The pump according to claim 2, wherein, The diameter of the second section is larger than the diameter of the first section.

4. The pump according to claim 1, wherein, Ceramic seals are provided above and below the high-pressure inlet and low-pressure outlet in the housing.

5. The pump according to claim 3, wherein, A discharge port is provided in the first section of the cylinder near the piston, and the discharge port communicates with the area of ​​the shell adjacent to the connecting rod.

6. The pump according to claim 5, wherein, It also includes a channel that extends from the evacuation port into the area of ​​the housing adjacent to the connecting rod.

7. The pump according to claim 1, wherein, It also includes a lubrication channel that extends through the piston and the connecting rod, with the end of the lubrication channel and the second end of the connecting rod spaced apart from the piston communicating with the angled plate.

8. The pump according to claim 7, wherein, A filter is provided in the lubrication channel.

9. The pump according to claim 1, wherein, The driving device is a motor.

10. The pump according to claim 1, wherein, The drive device is a source of fluid under pressure, which is operatively connected to the high-pressure inlet.

11. The pump according to claim 10, wherein, The source of the fluid under the pressure is a high-pressure pump.

12. The pump according to claim 11, wherein, The low-pressure outlet is operatively connected to the fluid inlet for the high-pressure pump.

13. The pump according to claim 1, wherein, The high-pressure inlet port and the low-pressure outlet port extend through the rotatable cylinder.

14. The pump according to claim 13, wherein, The high-pressure inlet and the low-pressure outlet are configured to be approximately perpendicular to the connecting rod.

15. The pump according to claim 1, wherein, The inlet port and the outlet port pass through the cylinder and communicate with the first end of the piston.

16. The pump according to claim 15, wherein, The inlet port and the outlet port are configured to be approximately perpendicular to the connecting rod.

17. The pump according to claim 16, wherein, The cylinder has a first end, which is positioned adjacent to the top of the shell.

18. The pump according to claim 17, wherein, A bearing recess is provided at the first end of the shell adjacent to the cylinder, and the flow channel connects the outlet port to the bearing recess, wherein the bearing recess forms a hydrostatic bearing between the first ends of the shell and the cylinder.

19. The pump according to claim 18, wherein, A needle valve is provided in the flow channel connecting the bearing recess and the outlet port. This needle valve controls the flow of fluid from the outlet port to the bearing recess.

20. The pump according to claim 15, wherein, A circumferential flow channel is provided, which has a first region connecting the cylinder to the outlet port and a second region connecting the cylinder to the inlet port.

21. The pump according to claim 20, wherein, The circumferential flow channel is provided with a first bearing section and a second bearing section to define the first region and the second region.

22. The pump according to claim 15, wherein, A first circumferential bearing recess and a second circumferential bearing recess are provided between the cylinder and the shell. The first circumferential bearing is connected to the high-pressure inlet, and the groove connects the first circumferential bearing recess and the second circumferential bearing recess.

23. The pump according to claim 22, wherein, The circumferential length of the second circumferential bearing recess is greater than that of the first circumferential bearing recess.

24. The pump according to claim 9, wherein, The angled plate is connected to the motor.

25. The pump according to claim 24, wherein, The motor has a shaft that is angled to the connecting rod of the piston.

26. An axial piston pump, comprising: The shell has an inlet port and an outlet port; A rotatable cylinder having a plurality of cylinders positioned in a housing, the cylinders being configured to communicate with the inlet port and the outlet port as the cylinder rotates, the inlet port and the outlet port extending through the rotatable cylinder; A piston, movably positioned in each of a plurality of cylinders, having a first end and a second end, wherein the first end of the piston communicates with the inlet port and the outlet port when the cylinders rotate; Multiple connecting rods having a first end and a second end, the first end of the connecting rods being connected to one of the pistons, the second end of the connecting rods being operatively engaged with an angled plate, the inlet port and the outlet port being configured to be substantially perpendicular to the connecting rods; A drive unit, operatively connected to the cylinder to rotate it, causes the piston to move in multiple cylinders when the angled plate moves the second connecting rod in the connecting rod.

27. The pump according to claim 26, wherein, It also includes a lubrication channel that extends through the piston and the connecting rod, with the end of the lubrication channel and the second end of the connecting rod communicating with the angled plate.

28. The pump according to claim 27, wherein, A filter is provided in the lubrication channel.

29. The pump according to claim 26, wherein, The driving device is a motor 30.

30. The pump according to claim 29, wherein, The motor has a shaft, the angled plate is mounted on the shaft, and the shaft is set at a certain angle to the connecting rod.

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