Internal combustion piston pump

Abstract

The invention discloses an internal combustion piston pump, and relates to the technical field of deep sea mining and conveying and long-distance conveying, a crankshaft is shared by a two-stroke internal combustion engine and a piston pump, and connecting rods of the piston pump are uniformly dispersed on corresponding crank throws of the internal combustion engine; the number of internal combustion engine cylinders and piston pump hydraulic cylinders, the length of connecting rods, the diameter of cylinder bodies and the center turning radius of a crank throw are reasonably calculated according to the required power configuration. According to the internal combustion piston pump, power output by the air cylinders of the internal combustion engine can be transmitted to the hydraulic cylinder of the piston pump to do work nearby, when the gas pressure in the stroke tail period of a certain air cylinder of the internal combustion engine is reduced or the suction stroke does not do work, the power is compensated by work of other air cylinders nearby, and therefore the maximum torque borne by all crank throws is basically equal; under the condition that the maximum torque borne by the crank throw is certain, larger power can be output; and the crankshaft only fills and supplements the power, and the torque needing to be transmitted is smaller, so that the requirement on the crankshaft is further reduced.

Description

Technical Field

[0001] The invention relates to the fields of deep sea mining and transportation technology and long distance transportation technology, and in particular to an internal combustion piston pump. Background Art

[0002] In deep-sea mining of polymetallic nodules, the height difference is very large and there is no way to connect the middle, so a large flow and high head pump is needed. For example, the design needs to transport 3000m 3 / h, the outlet pressure needs to be 25MPa. If a single pump is used for transportation, its installed power will reach 27,000 kilowatts, which is a huge challenge for motor manufacturing, inverter manufacturing, connecting shaft strength, transmission system manufacturing, etc.

[0003] If multiple pumps are used in parallel, on the one hand the efficiency will be reduced, and on the other hand the ship will be too crowded and many pumps will occupy a large area.

[0004] Furthermore, the ship needs an internal combustion engine to generate electricity. If it is driven by an electric motor, the following steps are required: 1. Internal combustion engine to generate electricity; 2. Step-up rectification and frequency conversion; 3. High-voltage motor drive; 4. Reducer to reduce the speed; 5. Piston pump transmission. This method has a long transmission chain, occupies a large area, and has a relatively low efficiency.

[0005] If steam is used to push the piston directly in a straight line, the steam pressure must be maintained at a very high pressure capable of pushing the piston at all times before exhausting the steam. Otherwise, the pressure may drop and the piston may not be pushed. In this case, the exhaust steam pressure will be very high, and a waste heat recovery power generation system will need to be built separately. However, it is questionable whether the ship can use up all the electricity generated by the waste heat, and it may have to be abandoned.

[0006] If the internal combustion engine is used for direct drive, the torque generated by multiple cylinders of the internal combustion engine needs to be gradually gathered to the coupling position. After being transmitted to the piston pump, it is gradually decomposed from the coupling position to the crankshaft where each piston is located, and then pushes the piston to do work. In this way, the crankshaft that transmits the maximum torque will bear several times more torque than the crankshaft that transmits the minimum torque. The manufacturing difficulty of the crankshaft increases and the power increase is limited.

[0007] Other projects such as reservoir dredging, river dredging, deep-sea filling, etc. face the same problems as on ships because of the remote construction sites or insufficient power of the local power grid. Summary of the invention

[0008] The purpose of the present invention is to provide an internal combustion piston pump to solve the problems existing in the above-mentioned prior art. A low-speed two-stroke internal combustion engine for ship or land use and a piston pump share a crankshaft, and a dispersed force transmission method is adopted. The torque to be transmitted is smaller, and the requirements for the crankshaft will be further reduced. At the same time, the manufacturing technical difficulty of the internal combustion engine crankshaft and the piston pump crankshaft is greatly reduced, and the bottlenecks encountered in the prior art are overcome.

[0009] To achieve the above-mentioned objectives, the present invention provides the following solution: The present invention provides an internal combustion piston pump, comprising a crankshaft, a plurality of piston pump hydraulic cylinders and a plurality of internal combustion engine cylinders, wherein the plurality of piston pump hydraulic cylinders and the plurality of internal combustion engine cylinders share the same crankshaft, and the connecting rods of the piston pump hydraulic cylinders are evenly and dispersedly connected to the corresponding cranks of the crankshaft of the internal combustion engine cylinders.

[0010] Preferably, the number of the internal combustion engine cylinders and the piston pump hydraulic cylinders is equal or unequal, the connecting rod lengths of the internal combustion engine cylinders and the piston pump hydraulic cylinders are equal or unequal, the cylinder body diameters of the internal combustion engine cylinders and the piston pump hydraulic cylinders are equal or unequal, and the center turning radius of each crank on the crankshaft is equal or unequal; the number of the internal combustion engine cylinders and the piston pump hydraulic cylinders, the connecting rod length, the cylinder body diameter and the center turning radius of the crank are calculated and configured according to the required power.

[0011] Preferably, the working time periods of the plurality of cylinders of the internal combustion engine are arranged in a step-like manner within the working stroke period of the adjacent piston pump hydraulic cylinder.

[0012] Preferably, a first sealing ring and a second sealing ring are provided on the outer periphery of the piston of the piston pump hydraulic cylinder. The first sealing ring is used to seal the conveying liquid when the piston pump hydraulic cylinder operates normally, and the second sealing ring is used to protect the crankcase from being contaminated by the leaking liquid when the first sealing ring leaks.

[0013] Preferably, a pressure relief ring groove is provided on the piston of the piston pump hydraulic cylinder between the first sealing ring and the second sealing ring. When leakage occurs during operation of the internal combustion piston pump, liquid leaking from the first sealing ring is guided to the leakage drain rod through the pressure relief ring groove and then discharged from the piston pump hydraulic cylinder.

[0014] Preferably, one end of the leakage drain rod is fixed on the piston of the piston pump hydraulic cylinder, and the drain channel in the middle of the leakage drain rod is connected to the pressure relief ring groove; the outer end of the leakage drain rod extends out of the piston pump hydraulic cylinder.

[0015] Preferably, the leakage drain rod is coaxially mounted with the piston of the piston pump hydraulic cylinder and moves synchronously with the piston.

[0016] Preferably, a sealing layer is provided between the outer end of the leakage drain rod and the pump body of the piston pump hydraulic cylinder.

[0017] Compared with the prior art, the present invention has achieved the following beneficial technical effects:

[0018] The internal combustion piston pump of the present invention adopts a two-stroke internal combustion engine and a piston pump to share a crankshaft, and the connecting rod of the piston pump is evenly distributed on the corresponding crank of the internal combustion engine. The number of cylinders of the internal combustion engine and the hydraulic cylinder of the piston pump does not need to be completely equal, the length of the connecting rod does not need to be completely equal, the diameter of the cylinder does not need to be completely equal, and the central rotation radius of each crank on the crankshaft does not need to be completely the same, and it is reasonably calculated according to the required power configuration. In this way, for each cylinder of the internal combustion engine, the power output by the cylinder no longer needs to be concentrated and gathered to the coupling for transmission, and can be transmitted to the piston pump nearby to do work. When the gas pressure at the end of a cylinder stroke of the internal combustion engine is reduced, or when the suction stroke does not do work, it is compensated by the work of other nearby cylinders. In this way, the maximum torque borne by each crank is basically equal. When the crank bears a certain maximum torque, it can output greater power; the crankshaft only fills in the power, and the torque to be transmitted is smaller, so the requirements for the crankshaft will be further reduced, and the manufacturing technology difficulty of the crankshaft of the internal combustion engine and the crankshaft of the piston pump is greatly reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0020] Figure 1 It is a schematic diagram of the structure of an internal combustion piston pump;

[0021] Figure 2 It is a schematic diagram of two seals of the piston of the piston pump hydraulic cylinder;

[0022] Among them, 1. the first internal combustion engine cylinder; 2. the second internal combustion engine cylinder; 3. the third internal combustion engine cylinder; 4. the piston pump hydraulic cylinder, 5. the leakage drain rod; 6. the sealing layer; 7. the first sealing ring; 8. the pressure relief ring groove; 9. the second sealing ring; 10. the crankshaft. DETAILED DESCRIPTION

[0023] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0024] The purpose of the present invention is to provide an internal combustion piston pump to solve the problems existing in the above-mentioned prior art. A low-speed two-stroke internal combustion engine for ship or land use and a piston pump share a crankshaft, and a dispersed force transmission method is adopted. The torque to be transmitted is smaller, and the requirements for the crankshaft will be further reduced. At the same time, the manufacturing technical difficulty of the internal combustion engine crankshaft and the piston pump crankshaft is greatly reduced, and the bottlenecks encountered in the prior art are overcome.

[0025] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0026] like Figure 1-Figure 2 As shown, the present invention provides an internal combustion piston pump, which adopts a method of dispersing the force transmission by using a cylinder of a low-speed two-stroke internal combustion engine for ships or land use and a piston pump hydraulic cylinder 4 to share a crankshaft 10.

[0027] The piston pump of the present invention is a general term for piston pumps and plunger pumps. For the sake of simplicity and clarity in description, they are collectively referred to as piston pumps.

[0028] The speed of a large ship or land-based low-speed two-stroke internal combustion engine is around 100rpm to 200rpm, which is also the normal operating speed of a piston pump. The piston pump is also a two-stroke, and the piston of the piston pump does not do work when it moves from the outer stop point to the inner stop point, which corresponds to the compression stroke of the internal combustion engine piston moving from the inner stop point to the outer stop point. The piston of the piston pump needs to receive power to do work outward when it moves from the inner stop point to the outer stop point, which corresponds to the work done by the gas when the internal combustion engine piston moves from the outer stop point to the inner stop point.

[0029] Internal combustion engines have many cylinders, and each cylinder corresponds to a crank on the crankshaft 10. Normally, the power of these cylinders needs to be gathered and then output in a concentrated manner. The torque borne near the coupling position is many times greater than that at the farthest end. The manufacturing of the crankshaft 10 is the main bottleneck in the manufacturing of internal combustion engines.

[0030] The piston pump also has many hydraulic cylinders, each of which corresponds to a crank on the crankshaft 10. The power of these hydraulic cylinders needs to be gathered and concentrated at the coupling position first and then output one by one. The torque close to the coupling position is many times greater than that at the farthest end. The manufacturing of the crankshaft 10 is also the main bottleneck in the manufacturing of piston pumps.

[0031] The present invention uses a two-stroke internal combustion engine and a piston pump to share a crankshaft 10. The connecting rods of the piston pump are evenly distributed on the corresponding cranks of the internal combustion engine. The number of cylinders of the internal combustion engine and the number of hydraulic cylinders 4 of the piston pump do not need to be completely equal, the lengths of the connecting rods do not need to be completely equal, the diameters of the cylinders do not need to be completely equal, and the central rotation radius of each crank on the crankshaft 10 does not need to be completely the same. It can be reasonably calculated based on the required power configuration.

[0032] In this way, for each cylinder of the internal combustion engine, the power output by the cylinder no longer needs to be concentrated and transmitted to the coupling, but can be transmitted to the nearby piston pump to do work. When the gas pressure decreases at the end of a cylinder stroke of the internal combustion engine, or when the intake stroke does not do work, it is compensated by the work of other nearby cylinders. In this way, the maximum torque that each crankshaft can withstand is basically equal. When the maximum torque that the crankshaft withstands is constant, greater power can be output.

[0033] If the angles of the piston pump hydraulic cylinder 4 and the internal combustion engine cylinder are arranged reasonably, the force of the internal combustion engine cylinder can even be directly transmitted to the piston of the piston pump hydraulic cylinder 4, and the crankshaft 10 only serves to fill in the power gap, and the torque to be transmitted is smaller, which further reduces the requirements for the crankshaft 10; this also greatly reduces the manufacturing technical difficulty of the internal combustion engine crankshaft 10 and the piston pump crankshaft 10, and overcomes the bottlenecks encountered by the two existing technologies.

[0034] The piston of the piston pump hydraulic cylinder 4 in the present invention is different from the piston of a general piston pump. There are a first sealing ring 7 and a second sealing ring 9 on the piston of the piston pump hydraulic cylinder 4. The first sealing ring 7 is responsible for sealing the conveying liquid when the piston pump hydraulic cylinder 4 is operating normally. The second sealing ring 9 is a protective seal that protects the crankshaft 10 box from being contaminated by the leaking liquid when the first sealing ring 7 leaks.

[0035] A pressure relief groove 8 is provided between the first sealing ring 7 and the second sealing ring 9. When leakage occurs during equipment operation, the liquid leaking from the first sealing ring 7 is decompressed in the pressure relief groove 8 and is drained through the opening to the leakage drain rod 5 to be discharged from the piston pump hydraulic cylinder 4.

[0036] The leakage drain rod 5 is fixed on the piston of the piston pump hydraulic cylinder 4. The hole in the middle of the leakage drain rod 5 is connected with the pressure relief ring groove 8 on the piston, so that the leaked liquid can be discharged from the pump.

[0037] The leakage drain rod 5 is coaxially installed with the piston of the piston pump hydraulic cylinder 4 and can move synchronously with the piston of the piston pump hydraulic cylinder 4 .

[0038] When the leakage drain rod 5 and the piston of the piston pump hydraulic cylinder 4 move synchronously, there is a sealing layer 6 between the leakage drain rod 5 and the pump body of the piston pump hydraulic cylinder 4, and leakage will not occur under normal circumstances.

[0039] Normally, no liquid is discharged from the leaking drain rod 5. When liquid is found to flow out of the leaking drain rod 5, it indicates that the piston seal of the piston pump hydraulic cylinder 4 is leaking. Timely maintenance will not pollute the crankcase of the internal combustion engine.

[0040] The internal combustion engine cylinder transmits power and the piston pump hydraulic cylinder 4 receives power in a decentralized and nearby manner, rather than in a centralized and centralized manner.

[0041] The crankshaft 10 corresponding to the internal combustion engine cylinder and the crankshaft 10 corresponding to the piston pump hydraulic cylinder 4 may be the same or different, and the cross-sectional diameter and the radius of gyration may be the same or different, and can be flexibly designed according to power calculation.

[0042] Embodiment 1

[0043] This embodiment provides an internal combustion piston pump, assuming that there are three internal combustion engine cylinders located on different cranks, and the internal combustion engine cylinders in the present invention are completely the same as the common internal combustion engine cylinders in principle and structure;

[0044] The piston pump hydraulic cylinder 4 is located on the same crankshaft 10 as the three internal combustion engine cylinders. Although the crankshaft 10 is the same, it can also be located on different cranks. There is no need to establish a one-to-one correspondence between the piston pump hydraulic cylinder 4 and the internal combustion engine cylinders, and can be flexibly designed based on actual power calculations.

[0045] by Figure 1 Take this as an example to illustrate: Figure 1 Assume that the ratio of the number of internal combustion engine cylinders and piston pump hydraulic cylinders 4 is 3:1. This description is only for the convenience of illustration. The engineering design is not based on this configuration. It is also necessary to calculate the working time and power superposition.

[0046] Assuming that the crankshaft 10 rotates counterclockwise, Figure 1 In the position shown, the piston in the piston pump hydraulic cylinder 4 has just passed the near dead center and is in the power stroke; the first internal combustion engine cylinder 1 has just passed the far dead center and is in the beginning of the power stroke. At this time, the mixed gas in the cylinder has just been ignited and the gas pressure is relatively high; the second internal combustion engine cylinder 2 has not reached the far dead center and is in the return stroke without power, but is close to the far dead center and is about to ignite; the third internal combustion engine cylinder 3 has not reached the far dead center and is in the return stroke without power, and is slightly far from the far dead center;

[0047] Since the liquid pressure fluctuation of the piston pump hydraulic cylinder 4 during the power stroke is very small, it is basically a constant pressure output, but not a constant power output. The power consumption of the power stroke basically changes according to the positive value of the sine curve. The return feed stroke does not do work and the power consumption is basically zero.

[0048] During the power stroke of the internal combustion engine cylinder, the cylinder pressure changes greatly, from the maximum when the far end point is just ignited to almost zero when the near end point is near the end point. No external work is done during the return stroke, and the compressed gas is required to consume power.

[0049] Ordinary internal combustion engines pursue stable power output, and generally the working periods of each cylinder are evenly arranged. The power of each cylinder is all aggregated to the coupling and output to the outside in a unified manner.

[0050] In the present invention, the working period of the cylinder of the internal combustion engine is concentrated in the working stroke period of the adjacent piston pump hydraulic cylinder 4 and arranged in steps. Figure 1In the embodiment, the piston in the piston pump hydraulic cylinder 4 is in the power stroke after passing the near dead point; however, the power consumption is relatively small at this time, and the remaining power of other cylinders of the internal combustion engine can be used to drive the piston.

[0051] As the piston pump hydraulic cylinder 4 moves forward, the power required to be consumed gradually increases. At this time, the first internal combustion engine cylinder 1 is ignited. When the internal combustion cylinder is just ignited, the cylinder pressure is relatively high and can independently push the piston forward.

[0052] As the crankshaft 10 rotates, the piston of the piston pump hydraulic cylinder 4 continues to move forward, the piston speed gradually increases, and the power consumed also gradually increases. At this time, the cylinder pressure in the first internal combustion engine cylinder 1 decreases, and the second internal combustion engine cylinder 2 begins to ignite and enters the power stroke.

[0053] The crankshaft 10 continues to rotate, and the piston of the piston pump hydraulic cylinder 4 continues to move forward. The cylinder pressure in the first internal combustion engine cylinder 1 drops to the end, and the air pressure in the second internal combustion engine cylinder 2 also drops significantly. At this time, the third internal combustion engine cylinder 3 ignites, pushing the piston of the piston pump to the far end point.

[0054] After the piston of the piston pump hydraulic cylinder 4 passes the far dead center, the return stroke basically consumes no power. At this time, the gas pressure in the second internal combustion engine cylinder 2 is already low, and the first internal combustion engine cylinder 1 has also reached the near dead center and started the compression stroke, which requires power consumption. The pressure in the third internal combustion engine cylinder 3 also decreases, and the remaining gas pressure in the cylinder pushes the first internal combustion engine cylinder 1 into the compression stroke, and the remaining power is output to other cranks on the crankshaft 10 that consume power.

[0055] In this case, most of the power of the nearest several internal combustion engine cylinders is consumed in the adjacent piston pump hydraulic cylinder 4, and only a small amount of power is transmitted to other power-consuming cranks of the crankshaft 10 in the form of torque to fill in the power.

[0056] The power output form of the crankshaft 10 is changed from the original centralized output to the nearby decentralized digestion of the present invention, which not only combines the internal combustion engine cylinder crankshaft 10 and the piston pump hydraulic cylinder 4 crankshaft 10 into one, but also reduces the maximum transmission power of the crankshaft 10, while saving the transmission system, saving power generation, substation, frequency conversion, electric motor, and gear reduction and other consumption links.

[0057] Embodiment 2

[0058] Take the 12-cylinder internal combustion engine cylinder corresponding to the 3-cylinder piston pump hydraulic cylinder 4 as an example.

[0059] For most conventional 12-cylinder internal combustion engines, the ignition sequence is usually 1-5-9-6-11-2-7-10-3-8-12-4, or 1-2-4-8-3-6-5-7-10-9-11. The ignition time interval is uniform, that is, one cylinder is ignited every 30° in this sequence. The ignited cylinders are arranged crosswise in order to achieve uniform and stable output power. At the same time, the maximum torque borne by the crankshaft 10 is uniform and stable.

[0060] For the present invention, the situation is different. During the working stroke of the piston pump hydraulic cylinder 4, the nearby internal combustion engine cylinders need to be ignited in a step-by-step manner, and the corresponding ignition sequence and ignition interval of the 12 internal combustion engine cylinders are very different.

[0061] Assuming that the 1# internal combustion engine cylinder, 2# internal combustion engine cylinder, 3# internal combustion engine cylinder, and 4# internal combustion engine cylinder push the 1# piston pump hydraulic cylinder nearby, the 5# internal combustion engine cylinder, 6# internal combustion engine cylinder, 7# internal combustion engine cylinder, and 8# internal combustion engine cylinder push the 2# piston pump hydraulic cylinder nearby, and the 9# internal combustion engine cylinder, 10# internal combustion engine cylinder, 11# internal combustion engine cylinder, and 12# internal combustion engine cylinder push the 3# piston pump hydraulic cylinder nearby, and the near dead point of the 1# piston pump hydraulic cylinder is 0°, then the power consumed by the 1# piston pump hydraulic cylinder is P=FV=ps The positive part of rsinθ, where P is the power consumption, p is the pressure of the piston pump hydraulic cylinder, V is the piston running speed of the piston pump hydraulic cylinder, s is the piston diameter of the piston pump hydraulic cylinder, θ is the crankshaft angle, and r is the crankshaft rotation radius; the power consumed by the 2# piston pump hydraulic cylinder is the positive part of P=FV=psrsin(θ+120), and the power consumed by the 3# piston pump hydraulic cylinder is the positive part of P=FV=psrsin(θ+240). It can be seen that the power demand of the piston pump hydraulic cylinder is not balanced, but fluctuates.

[0062] For the cylinder of an internal combustion engine, the work done is also unbalanced, and the pressure of the cylinder of the internal combustion engine changes rapidly from the maximum value to near normal pressure.

[0063] For the 1# piston pump hydraulic cylinder, the power consumed is P=FV=psrsinθ positive part. If the 1# internal combustion engine cylinder is ignited at θ=0°, the power consumed by the 1# piston pump hydraulic cylinder is close to 0 at the beginning. The output power of the 1# internal combustion engine cylinder can also help other internal combustion engine cylinders to fill in the power. As the 1# piston pump hydraulic cylinder moves and consumes power and rises along the sine curve, for example, when it reaches θ=35°, the power of the 1# internal combustion engine cylinder decreases, which is not enough to support the power consumption of the 1# piston pump hydraulic cylinder. At this time, the 2# internal combustion engine cylinder ignites; when it reaches θ=80°, the output power of the first two internal combustion engine cylinders decreases and is not enough to support the power consumption of the 1# piston pump hydraulic cylinder. At this time, the 3# internal combustion engine cylinder ignites. After θ=90°, the power consumption of the piston pump hydraulic cylinder begins to decrease. Although the output power of the three internal combustion engine cylinders ignited in front has dropped a lot, it can still last for a period of time; when it reaches θ=135°, the fourth internal combustion engine cylinder ignites, and the four internal combustion engine cylinders work together to push the piston pump hydraulic cylinder to the far end point.

[0064] After the 1# piston pump hydraulic cylinder reaches the far dead point, it enters the suction stroke. At this time, almost no power is consumed in half a cycle. The remaining power of the first four internal combustion engine cylinders is transferred to other internal combustion engine cylinders or piston pump hydraulic cylinders that need to consume power through the crankshaft 10 for filling. After the first four internal combustion engine cylinders reach the near dead point in turn, they enter the scavenging compression stroke in turn, which consumes power but does not do work externally.

[0065] The other piston pump hydraulic cylinders and internal combustion engine cylinders are similar to those described above.

[0066] It can be seen from this that the ignition time interval of each cylinder of the internal combustion engine is not fixed, but is configured according to the actual power consumption of the piston pump hydraulic cylinder 4.

[0067] The above ignition angles are not the final ignition angles and need to be specifically calculated and arranged based on actual power consumption.

[0068] It should be noted that it is obvious to those skilled in the art that the present invention is not limited to the details of the above exemplary embodiments, and that the present invention can be implemented in other specific forms without departing from the spirit or essential features of the present invention. Therefore, no matter from which point of view, the embodiments should be regarded as exemplary and non-restrictive, and the scope of the present invention is defined by the appended claims rather than the above description, and it is intended that all changes falling within the meaning and scope of the equivalent elements of the claims are included in the present invention, and any figure mark in the claims should not be regarded as limiting the claims involved.

[0069] The present invention uses specific examples to illustrate the principles and implementation methods of the present invention. The above examples are only used to help understand the method and core ideas of the present invention. At the same time, for those skilled in the art, according to the ideas of the present invention, there will be changes in the specific implementation methods and application scope. In summary, the content of this specification should not be understood as limiting the present invention.

Claims

1. An internal combustion piston pump, characterized in that: It comprises a crankshaft, a plurality of piston pump hydraulic cylinders and a plurality of internal combustion engine cylinders. The plurality of piston pump hydraulic cylinders and the plurality of internal combustion engine cylinders share the same crankshaft, and the connecting rods of the piston pump hydraulic cylinders are evenly and dispersedly connected to the corresponding cranks of the crankshafts of the internal combustion engine cylinders.

2. The internal combustion piston pump according to claim 1, characterized in that: The number of the internal combustion engine cylinders and the piston pump hydraulic cylinders is equal or unequal, the connecting rod lengths of the internal combustion engine cylinders and the piston pump hydraulic cylinders are equal or unequal, the cylinder body diameters of the internal combustion engine cylinders and the piston pump hydraulic cylinders are equal or unequal, and the central turning radius of each crank on the crankshaft is equal or unequal; the number of the internal combustion engine cylinders and the piston pump hydraulic cylinders, the connecting rod length, the cylinder body diameter and the central turning radius of the crank are calculated and configured according to the required power.

3. The internal combustion piston pump according to claim 1, characterized in that: The working time periods of the plurality of internal combustion engine cylinders are arranged in a step-like manner within the working stroke time period of the adjacent piston pump hydraulic cylinders.

4. The internal combustion piston pump according to claim 1, characterized in that: The outer periphery of the piston of the piston pump hydraulic cylinder is provided with a first sealing ring and a second sealing ring. The first sealing ring is used to seal the conveying liquid when the piston pump hydraulic cylinder is operating normally, and the second sealing ring is used to protect the crankcase from being contaminated by the leaking liquid when the first sealing ring leaks.

5. The internal combustion piston pump according to claim 4, characterized in that: A pressure relief ring groove is provided on the piston of the piston pump hydraulic cylinder between the first sealing ring and the second sealing ring. When leakage occurs during operation of the internal combustion piston pump, the liquid leaking from the first sealing ring is guided to the leakage drain rod through the pressure relief ring groove and then discharged from the piston pump hydraulic cylinder.

6. The internal combustion piston pump according to claim 5, characterized in that: One end of the leakage drain rod is fixed on the piston of the piston pump hydraulic cylinder, and the drain channel in the middle of the leakage drain rod is connected with the pressure relief ring groove; the outer end of the leakage drain rod extends out of the piston pump hydraulic cylinder.

7. The internal combustion piston pump according to claim 6, characterized in that: The leakage drain rod is coaxially mounted with the piston of the piston pump hydraulic cylinder and moves synchronously with the piston.

8. The internal combustion piston pump according to claim 6, characterized in that: A sealing layer is arranged between the outer end of the leakage drain rod and the pump body of the piston pump hydraulic cylinder.

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