A hydraulic centrifugal compressor

Abstract

This invention relates to the field of compressor technology and discloses a hydraulic centrifugal compressor, comprising a centrifugal pump, a potential energy receiving device, a piston cylinder, and a reversing valve. The centrifugal pump includes a pump casing, a main shaft, and impellers, with a liquid-containing chamber within the pump casing. The potential energy receiving device includes an outer annular chamber, within which a receiving wheel is rotatably mounted, with receiving blades arranged on the receiving wheel. The pump casing has an outlet and a return port. The piston cylinder includes a hydraulic chamber, a pneumatic chamber, and a hydraulic piston. The hydraulic chamber has a first flow channel and a second flow channel, with the first flow channel located on the side of the hydraulic piston closer to the centrifugal pump and the second flow channel located on the side of the hydraulic piston closer to the pneumatic chamber. The reversing valve includes a valve core and a liquid direction control switch, with the valve core having a compression position and a recovery position. The movement of the hydraulic piston is driven by liquid, allowing the liquid pressure to be output to the hydraulic piston, simultaneously utilizing the kinetic potential energy and pressure energy generated by the centrifugal pump to achieve energy saving.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a hydraulic centrifugal compressor. Background Technology

[0002] Compressors are commonly used fluid machines in modern equipment and are the core equipment of refrigeration systems. They draw in low-temperature, low-pressure refrigerant gas through the suction pipe, compress it by a piston driven by a motor, and then discharge high-temperature, high-pressure refrigerant gas through the discharge pipe, providing power for the refrigeration cycle.

[0003] Existing general-purpose compressors are directly driven by an electric motor during operation, causing the crankshaft to rotate, which in turn drives the connecting rod to reciprocate the piston, resulting in changes in cylinder volume. Direct motor drive leads to significant energy loss and requires a speed reduction device. To increase the compressor's compression speed, the electric motor's output power needs to be increased. High-power compressors require multiple compression chambers, resulting in larger size, higher cost, and greater energy loss.

[0004] A centrifugal pump is a power device that uses the high-speed rotation of a liquid to output power. By using a centrifugal pump to lift the liquid from a static or low speed to a high speed, the liquid has kinetic and potential energy when rotating at high speed. At the same time, the liquid is incompressible. Using the liquid to drive the piston of the compressor can greatly increase the compression speed and improve the working efficiency. Summary of the Invention

[0005] The purpose of this invention is to provide a hydraulic centrifugal compressor to solve the problems of existing compressors that are directly driven by electric motors, resulting in large size, high power consumption, and high cost.

[0006] To achieve the above objectives, the present invention provides a hydraulic centrifugal compressor, including a centrifugal pump, a potential energy receiving device, and a piston cylinder communicating with the centrifugal pump. The centrifugal pump includes a pump housing, a main shaft rotatably mounted in the pump housing, and a vane anti-rotating mounted on the main shaft. The pump housing has a liquid-containing chamber for containing liquid.

[0007] The potential energy receiving device includes an outer ring chamber that communicates with the liquid-containing cavity. A receiving wheel is rotatably mounted inside the outer ring chamber, and receiving blades are arranged on the receiving wheel. The pump casing has an outlet that communicates with the outer ring chamber and a return port that communicates with the liquid-containing cavity.

[0008] The piston cylinder includes a hydraulic chamber, a pneumatic chamber, and a hydraulic piston, with one end of the hydraulic piston located in the hydraulic chamber and the other end located in the pneumatic chamber;

[0009] The hydraulic chamber is provided with a first flow channel and a second flow channel. The first flow channel is arranged on the side of the hydraulic piston near the centrifugal pump, and the second flow channel is arranged on the side of the hydraulic piston near the pneumatic chamber.

[0010] The hydraulic centrifugal compressor further includes a reversing valve, which includes a valve core movably arranged in the pump housing and a liquid direction control switch. The valve core has a compression position in its stroke where the outlet communicates with the first flow channel and the return port communicates with the second flow channel, and a recovery position where the outlet communicates with the second flow channel and the return port communicates with the first flow channel. The liquid direction control switch is used to control the movement direction of the reversing valve.

[0011] Preferably, the liquid direction control switch includes a valve stem arranged parallel to the valve core, a valve head at one end of the valve stem, and power flow channels at both axial ends of the valve core. The valve head has a reversing flow channel connecting the power flow channel to the outlet and return port for liquid-driven axial movement of the valve core. A first stop and a second stop extending into the hydraulic chamber are also arranged at the end of the valve stem away from the valve head. The first stop is located on the side of the hydraulic piston closer to the centrifugal pump, and the second stop is located on the side of the hydraulic piston closer to the pressure chamber. The hydraulic piston has the following characteristics during its stroke: The valve stem is moved to a first limit position by impacting the first stop to push it to move axially, and to a second limit position by impacting the second stop to push it to move axially. When the hydraulic piston is at the first limit position, the outlet is connected to the first power flow channel of the valve core near the centrifugal pump end, and the return port is connected to the second power flow channel of the valve core near the hydraulic chamber end, so that the valve core moves to the compression position. When the hydraulic piston is at the first limit position, the outlet is connected to the second power flow channel of the valve core near the hydraulic chamber end, and the return port is connected to the first power flow channel of the valve core near the centrifugal pump end, so that the valve core moves to the recovery position.

[0012] Preferably, the valve stem has a through central shaft hole, and the valve stem has a radially extending connecting hole that communicates with the central shaft hole. The connecting hole is located at one end of the valve head near the hydraulic chamber.

[0013] Preferably, both the first stop and the second stop are stop arms vertically arranged on the valve stem, and the stop arms are L-shaped, with the stop arms of the first stop and the second stop arranged opposite to each other.

[0014] Preferably, the pump casing is further provided with a speed-increasing gear set that meshes with the receiving wheel, and the speed-increasing gear set is connected to the main shaft by a one-way gear meshing.

[0015] Preferably, the liquid-containing chamber has an inner wall whose diameter gradually decreases along the direction from the centrifugal pump to the hydraulic chamber, and the constricted end of the inner wall is connected to the return port.

[0016] Preferably, the flap wheel has a hollow structure and a cavity separated from the liquid-containing cavity.

[0017] Preferably, the leaf wheel includes a main body and leaf blades arranged at one axial end of the main body, wherein multiple leaf blades are evenly distributed at intervals along the circumference of the main body, and the cavity is arranged on the main body.

[0018] Preferably, the inner wall of the flap wheel has a liquid channel extending along the axial direction of the flap wheel.

[0019] Preferably, there is a radial gap between the body and the inner wall of the pump casing.

[0020] Compared with existing technologies, the hydraulic centrifugal compressor of this invention has the following advantages: The piston cylinder has a hydraulic chamber and a pneumatic chamber. The outlet and return port of the centrifugal pump are connected to the first and second flow channels of the hydraulic chamber through a reversing valve. The reversing valve changes the flow direction of the liquid. When the compressor starts, the main shaft drives the impeller to rotate. The liquid in the liquid chamber rotates at high speed under the action of the impeller, possessing pressure energy and potential energy. The liquid passes through the outlet, enters the hydraulic chamber through the reversing valve, and drives the hydraulic piston to move. The hydraulic piston squeezes the liquid on the other side and returns it to the liquid chamber through the return port, forming a liquid circulation. Simultaneously, the liquid direction control switch controls the valve core of the reversing valve to move back and forth between the compression and recovery positions, thereby driving the hydraulic piston to move back and forth and compressing the gas in the pneumatic chamber. Utilizing the centrifugal force generated by the centrifugal pump on the liquid as a power source to drive the piston to reciprocate is more energy-efficient than directly converting an electric motor into reciprocating motion. All the kinetic energy generated by the centrifugal pump on the liquid is recovered and utilized. Compared with when it is not utilized, the generated kinetic energy is greater. The energy generated by the centrifugal pump is used multiple times, greatly improving the energy utilization rate and saving energy. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the structure of the hydraulic centrifugal compressor of the present invention when the piston is in the first extreme position;

[0022] Figure 2 This is a schematic diagram of the structure of the hydraulic centrifugal compressor of the present invention when the piston is in the second limit position;

[0023] Figure 3 This is a schematic diagram of the assembly of the speed-increasing gear set and the centrifugal pump in the hydraulic centrifugal compressor of the present invention;

[0024] Figure 4 yes Figure 3 A schematic diagram of the speed-increasing gear set and the transmission of the centrifugal pump;

[0025] Figure 5 This is a schematic diagram of the impeller structure of the hydraulic centrifugal compressor of the present invention;

[0026] Figure 6 yes Figure 5 A top view of the page wheel;

[0027] Figure 7 yes Figure 5 Side view of the page wheel;

[0028] Figure 8 yes Figure 5 A-a sectional view of the page wheel;

[0029] Figure 9 yes Figure 5 The b-b cross-sectional view of the leaf wheel;

[0030] Figure 10 yes Figure 6 A C-C sectional view of the leaf wheel;

[0031] Figure 11 yes Figure 5 d-d section view of the leaf wheel;

[0032] Figure 12 yes Figure 7 e-e sectional view of the page wheel;

[0033] Figure 13 This is a schematic diagram of the receiving wheel of the hydraulic centrifugal compressor of the present invention;

[0034] Figure 14 yes Figure 13 A top view of the receiving wheel;

[0035] Figure 15 yes Figure 14 A cross-sectional view of the receiving wheel.

[0036] In the diagram, 1 is the centrifugal pump; 11 is the pump casing; 111 is the outer annular chamber; 112 is the outlet; 113 is the return port; 12 is the main shaft; 13 is the impeller; 131 is the main body; 132 is the blade; and 133 is the cavity. 134. Liquid passage; 14. Speed-increasing gear set; 15. Receiving wheel; 151. Receiving blade; 152. Receiving wheel gear; 16. One-way gear; 2. Piston cylinder; 21. Hydraulic chamber; 211. First flow channel; 212. Second flow channel; 22. Pneumatic chamber; 23. Hydraulic piston; 3. Reversing valve; 31. Valve core; 311. First power flow channel; 312. Second power flow channel; 32. Valve stem; 321. Central shaft hole; 322. Connecting hole; 33. Valve head; 331. Reversing flow channel; 34. First stop; 35. Second stop; 4. Pneumatic pipeline; 41. Gas inlet; 42. Gas outlet; 43. One-way valve. Detailed Implementation

[0037] The specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and are not intended to limit the scope of the invention.

[0038] A preferred embodiment of the hydraulic centrifugal compressor of the present invention, such as... Figures 1 to 15 As shown in the figure, the arrows indicate the direction of motion of the corresponding objects. This hydraulic centrifugal compressor includes a centrifugal pump 1, a potential energy receiving device, a speed-increasing gear set 14, a piston cylinder 2, and a reversing valve 3. The centrifugal pump and piston cylinder 2 are arranged in parallel. A pneumatic pipeline 4 is also arranged on the piston cylinder 2, with a gas inlet 41 and a gas outlet 42. The centrifugal pump drives the piston cylinder 2, which compresses the gas input into the pneumatic pipeline 4. One-way valves 43 are arranged at the gas inlet 41 and the gas outlet 42 of the pneumatic pipeline 4 to ensure unidirectional gas flow; gas can only enter the pressure chamber 22 through the gas inlet 41 and exit the pressure chamber 22 through the gas outlet 42.

[0039] The centrifugal pump 1 includes a pump casing 11, a main shaft 12, and a vane 13. The inner cavity of the pump casing 11 forms a liquid-containing chamber. The main shaft 12 is rotatably mounted on the pump casing 11, with one end extending to the outside of the pump casing 11. A pulley is arranged on the main shaft 12 for connecting to an external motor, which drives the main shaft 12 to rotate. The vane 13 is anti-rotatingly mounted to the main shaft 12 and rotates with the main shaft 12, driving the liquid flow within the liquid-containing chamber.

[0040] The flap wheel 13 includes a main body 131 and flaps 132 arranged at one axial end of the main body 131. The flaps 132 are arranged at the end of the main body 131 near the piston cylinder 2, and multiple flaps 132 are evenly distributed circumferentially along the main body 131. The main body 131 and the main shaft 12 are anti-rotationally assembled via a keyway structure. The main body 131 has a hollow structure and a cavity 133 separated from the liquid chamber. The cavity 133 can contain air, inert gas, or a vacuum. The flap wheel 13 is made of a low-density metal material such as aluminum alloy. The density of the flap wheel 13 with the cavity 133 is less than the density of the liquid in the liquid chamber, so the flap wheel 13 will float on the liquid when placed in the liquid.

[0041] The body 131 of the impeller 13 has a central hole with an inner diameter equal to the outer diameter of the main shaft 12. An axially extending liquid channel 134 exists between the body 131 and the main shaft 12. The liquid channel 134 is located on the wall of the central hole of the impeller 13, and multiple liquid channels 134 are arranged at intervals along the circumference of the impeller 13. The liquid channel 134 is a rectangular groove. The liquid channel 134 connects to allow liquid to enter between the impeller 13 and the pump housing 11. When the impeller 13 rotates, the liquid passes through the liquid channel 134 and enters the radial gap between the body 131 and the main shaft 12. Under centrifugal force, it flows into the outer annular chamber 111.

[0042] There is a radial gap between the body 131 of the impeller 13 and the inner wall of the pump housing 11. When the impeller 13 rotates, the liquid in this gap rotates synchronously with the impeller 13 at high speed. If the impeller 13 vibrates or becomes eccentric, the gap between the impeller 13 and the pump housing 11 will change. Since the pump housing 11 is fixed, the impeller 13 is unlikely to vibrate or become eccentric when rotating at high speed, thus playing a centering role.

[0043] The potential energy receiving device is arranged inside the pump casing 11. The potential energy receiving device includes an outer ring chamber 111 and a receiving wheel 15. The outer ring chamber 111 is connected to the liquid chamber. The outer ring chamber 111 is arranged on the pump casing 11 and coaxially with the main shaft 12. When the impeller 13 rotates, it drives the liquid to rotate at high speed. The high-pressure liquid enters the outer ring chamber 111 through the channel.

[0044] The receiving wheel 15 is arranged within the outer ring chamber 111 and is rotatably mounted within the outer ring chamber 111 via bearings. The receiving wheel 15 is coaxially arranged with the main shaft 12. The receiving wheel 15 has a ring structure, with its inner wall surface fixedly connected to the outer ring of the bearing, and its outer circumferential surface connected to the speed-increasing gear set 14 via gear meshing. When the receiving wheel 15 rotates, it can drive the speed-increasing gear set 14 to rotate via the gears.

[0045] Multiple receiving blades 151 are arranged on the side of the receiving wheel 15. These blades are evenly spaced along the circumference of the receiving wheel 15 and are shaped like fish scales. There is a gap between adjacent receiving blades 151 to allow liquid flow; this gap is parabolic. The total cross-sectional area of ​​the liquid flow channels between the receiving blades 151 is larger than the cross-section at the outlet of the liquid chamber. The outlet of the liquid chamber is annular with no obstructions in the middle. When the wheel 13 rotates, it drives the liquid to rotate at high speed and enter the outer annular chamber 111. The liquid flows through the gap between adjacent receiving blades 151. When the liquid comes into contact with the receiving blades 151, the flow direction is changed by the receiving blades 151. Simultaneously, the liquid exerts a force on the receiving blades 151, driving them to rotate around the main shaft 12. The receiving blades 151 drive the receiving wheel 15 to rotate, which in turn drives the speed-increasing gear set 14 to rotate.

[0046] A speed-increasing gear set 14 is arranged inside the pump casing 11. The speed-increasing gear set 14 and the reversing valve 3 are respectively arranged on both sides of the main shaft 12. The speed-increasing gear set 14 includes seven sets of sequentially meshing gears. Six sets are equipped with a large gear, a small gear, and a shaft, respectively. Starting from the centrifugal pump 1, the large gear meshes with the small gear of the next set of gears. The ratio of the large gear to the small gear is approximately 2:1. The input gear of the speed-increasing gear set 14 is meshed with the receiving wheel 15. The receiving blade 151 drives the receiving wheel 15 to rotate under the pressure of the liquid. The receiving wheel 15 drives the speed-increasing gear set 14 to rotate. The output gear of the speed-increasing gear set 14 is meshed with the main shaft 12 through a one-way gear 16. The one-way gear 16 is arranged at the end of the main shaft 12 away from the vane 13. The one-way gear 16 is fixedly mounted on the main shaft 12 and is equipped with a one-way bearing. The one-way gear is connected to the outer ring of the one-way bearing to prevent rotation. The one-way gear achieves one-way rotation prevention through the one-way bearing.

[0047] When the centrifugal pump 1 is first started, the liquid velocity is relatively low, and the rotational speed of the main shaft 12 is greater than the speed of the output gear of the speed-increasing gear set 14. At this time, the one-way gear 16 idles. After the liquid velocity increases, the liquid drives the speed-increasing gear set 14 to rotate through the receiving wheel 15. The speed of the output gear of the speed-increasing gear set 14 is greater than the speed of the main shaft 12, and the one-way gear 16 rotates in the forward direction. At this time, the output gear of the speed-increasing gear set 14 drives the main shaft 12 to rotate through the one-way gear 16, thereby increasing the rotational speed of the main shaft 12, thereby further increasing the liquid velocity and thus increasing the pressure energy and potential energy of the liquid. The liquid continues to drive the main shaft 12 to rotate at high speed through the receiving wheel 15 and the speed-increasing gear set 14, and the impeller 13 further increases the liquid velocity, thereby improving the output efficiency of the centrifugal pump and thus improving working efficiency.

[0048] The pump casing 11 has an outlet 112 and a return port 113. The outlet 112 is connected to the outer annular chamber 111. After the liquid enters the outer annular chamber 15 under the action of the impeller 13, it flows into the hydraulic chamber 21 through the outlet 112 and the reversing valve 3. The return port 113 is located on the wall of the liquid-containing chamber. The liquid-containing chamber has an inner wall whose diameter gradually decreases along the direction from the centrifugal pump 1 to the piston cylinder 2. Specifically, the cross-section of the inner wall is a funnel-shaped structure, and the constricted end of the inner wall is connected to the return port 113. The return port 113 is used to allow the liquid in the hydraulic chamber 21 to flow back to the liquid-containing chamber. The funnel-shaped inner wall can buffer the liquid, making the liquid flow uniform. It can also prevent the high-speed rotating liquid in the liquid-containing chamber from flowing back to the return port 113, causing energy loss and transmitting pressure to the return port, thus preventing the output of pressure energy.

[0049] The piston cylinder 2 includes a hydraulic chamber 21, a pneumatic chamber 22, and a hydraulic piston 23. The hydraulic chamber 21 and the pneumatic chamber 22 are arranged adjacent to each other, and the hydraulic piston 23 is arranged between the hydraulic chamber 21 and the pneumatic chamber 22. One end of the hydraulic piston 23 is located in the hydraulic chamber 21 and the other end is located in the pneumatic chamber 22. The hydraulic chamber 21 is connected to the liquid chamber of the centrifugal pump 1. Liquid enters the hydraulic chamber 21 from the liquid chamber and drives the hydraulic piston 23 to move back and forth. The end of the hydraulic piston 23 located in the pneumatic chamber 22 compresses the gas entering from the gas inlet 41 of the pneumatic pipeline 4. After being compressed, the gas is discharged through the gas outlet 42.

[0050] The hydraulic chamber 21 has a first flow channel 211 and a second flow channel 212. The first flow channel 211 is arranged on the side of the hydraulic piston 23 near the centrifugal pump, and the second flow channel 212 is arranged on the side of the hydraulic piston 23 near the pneumatic chamber 22. That is, the liquid in the first flow channel 211 and the second flow channel 212 exert pressure on the hydraulic piston 23 in opposite directions after flowing out, so as to drive the hydraulic piston 23 to reciprocate.

[0051] A reversing valve 3 is arranged between the centrifugal pump 1 and the piston cylinder 2. The outlet 112 and return port 113 on the pump housing 11 are connected to the first flow channel 211 and the second flow channel 212 in the hydraulic chamber 21 through the reversing valve 3. The reversing valve 3 includes a valve core 31 and a liquid direction control switch. The reversing valve 3 is a four-way reversing valve. The valve core 31 is axially movable and assembled in the pump housing 11. The valve core 31 is used to switch the liquid flow channels between the outlet 112, the return port 113, the first flow channel 211, and the second flow channel 212 to change the movement direction of the hydraulic piston 23.

[0052] The valve core 31 is a four-way valve core, arranged parallel to the main shaft 12 of the centrifugal pump 1. When the valve core 31 moves axially to the side near the hydraulic chamber 21, the outlet 112 is connected to the first flow channel 211 through the valve core 31, and the return port 113 is connected to the second flow channel 212. At this time, the hydraulic piston 23 performs a compression motion, and the valve core 31 is in the compression position during its stroke. The hydraulic piston 23 compresses the gas in the pressure chamber 22. When the valve core 31 moves axially to the side near the centrifugal pump 1, the outlet 112 is connected to the second flow channel 212 through the valve core 31, and the return port 113 is connected to the first flow channel 211. At this time, the hydraulic piston 23 performs a retraction motion, and the valve core 31 is in the retraction position during its stroke. The pressure in the pressure chamber 22 decreases, and the outside gas enters the pressure chamber 22 through the gas inlet 41, waiting to be compressed by the hydraulic piston 23.

[0053] The valve core 31 has power flow channels arranged at both ends of its axial direction, which are connected to the outlet 112 and the return port 113, respectively. The power flow channel of the valve core 31 near the centrifugal pump 1 is defined as the first power flow channel 311 and the power flow channel near the piston cylinder 2 is defined as the second power flow channel 312. The liquid direction control switch is used to control the connection path between the outlet 112, the return port 113 and the first power flow channel 311 and the second power flow channel 312 at both ends of the valve core 31 to drive the valve core 31 to move.

[0054] The liquid direction control switch includes a valve stem 32, a valve head 33, a first stop 34, and a second stop 35, all of which are integrally formed. The valve stem 32 is arranged parallel to the valve core 31. The valve head 33 is located at the end of the valve stem 32 closest to the centrifugal pump, while the first stop 34 and the second stop 35 are located at the end of the valve stem 32 furthest from the valve head 33. The first stop 34 is located on the side of the hydraulic piston 23 closest to the centrifugal pump, and the second stop 35 is located on the side of the hydraulic piston 23 closest to the pressure chamber 22. That is, the first stop 34 and the second stop 35 are located on both axial sides of the hydraulic piston 23 within the hydraulic chamber 21, so that the hydraulic piston 23 drives the valve stem 32 to reciprocate via the first stop 34 and the second stop 35.

[0055] Both the first stop 34 and the second stop 35 are stop arms vertically arranged on the valve stem 32. The stop arms have an L-shaped structure, with one side perpendicular to the valve stem 32 and the other side parallel to it. The side of the stop arm parallel to the valve stem 32 extends into the hydraulic chamber 21. The sides of the first stop 34 and the second stop 35 parallel to the valve stem 32 are arranged opposite each other. When the hydraulic piston 23 reciprocates within the hydraulic chamber 21, it is axially stopped by the first stop 34 and the second stop 35, respectively. The first stop 34 and the second stop 35 drive the valve stem 32 to reciprocate, thereby causing the liquid to drive the valve core 31 to reciprocate axially.

[0056] The valve stem 32 is a hollow structure with an axially penetrating central bore 321 inside. A radially extending connecting hole 322, which communicates with the central bore 321, is also present on the valve stem 32. The connecting hole 322 is located at the end of the valve head 33 near the hydraulic chamber 21, i.e., at the axial center of the valve stem 32. The central bore 321 and the connecting hole 322 ensure that the fluid pressure between the two axial ends of the valve head 33 and the end of the valve stem 32 furthest from the valve head 33 is equal. The fluid can circulate within the connecting hole 322 and the central bore 321, reducing the frictional resistance of the valve head 33 and valve stem 32 movement and preventing resistance caused by the incompressible fluid. This ensures that the piston can pass through the first stop 34 and the second stop 35 to drive the valve stem 32 and valve head 33 axially.

[0057] A reversing flow channel 331 is provided on the valve head 33. The reversing flow channel 331 is connected to the first power flow channel 311 at one axial end of the valve core 31. The other interface of the valve head 33 is connected to the second power flow channel 312. When the valve head 33 moves axially back and forth under the action of the valve stem 32, it changes the connection relationship between the first power flow channel 311, the second power flow channel 312 and the liquid outlet 112 and the liquid return port 113, so that the liquid drives the valve core 31 to move axially back and forth.

[0058] When the outlet 112 is connected to the second flow channel 212 and the return port 113 is connected to the first flow channel 211, the hydraulic piston 23 moves towards the side closer to the centrifugal pump. The hydraulic piston 23 strikes the first stop 34, which drives the valve stem 32 and valve head 33 to move towards the side of the centrifugal pump. At this time, the hydraulic piston 23 is at the first limit position. When the hydraulic piston 23 is at the first limit position, the outlet 112 is connected to the first power flow channel 311 near the centrifugal pump end of the valve core 31, and the return port 113 is connected to the second power flow channel 312 near the hydraulic chamber 21 end of the valve core 31. At this time, after the liquid flows out from the outlet 112, it pushes the valve core 31 to move towards the side closer to the hydraulic chamber 21. When it reaches the end, the outlet 112 is connected to the first channel 211; the return port 113 is connected to the second flow channel 212, pushing the hydraulic piston 23 to move towards the pressure chamber 22 (see...). Figure 1 ).

[0059] When the hydraulic piston 23 moves to the side near the pressure chamber 22, it strikes the second stop 35. The second stop 35 drives the valve stem 32 and valve head 33 to move towards the side of the pressure chamber 22. When it reaches its limit, the hydraulic piston 23 is at its second extreme position. When the hydraulic piston 23 is at its second extreme position, the outlet 112 is connected to the second power flow channel 312 near the pressure chamber end of the valve core 31, and the return port 113 is connected to the first power flow channel 311 near the centrifugal pump end of the valve core 31. At this time, liquid flows out from the outlet 112 and pushes the valve core 31 to move towards the side near the centrifugal pump. The outlet 112 flows through the valve core 31 and the second flow channel 212, and the return port 113 flows through the valve core 31 and the first flow channel 211. The valve core 31 is in the retracted position. This pushes the hydraulic piston 23 to move towards the centrifugal pump (see...). Figure 2 (Complete one work cycle; see next work cycle) Figure 1 And so the cycle continues.

[0060] When the hydraulic piston 23 reciprocates, the first stop 34 and the second stop 35 drive the valve stem 32 and the valve head 33 to reciprocate. When the valve head 33 reciprocates, it changes the connection between the outlet 112, the return port 113 and the first power flow channel 311 and the second power flow channel 312 at both ends of the valve core 31, causing the valve core 31 to reciprocate axially. When the valve core 31 reciprocates axially, it changes the connection between the liquid flow channels of the outlet 112, the return port 113, the first flow channel 211 and the second flow channel 212, and then drives the hydraulic piston 23 to reciprocate, completing the working cycle and compressing the gas in the pressure chamber 22 to achieve the purpose of compressing the gas.

[0061] Existing compressor technology uses an electric motor to directly drive the piston, converting rotational energy into reciprocating motion. This results in significant energy loss and requires a speed reduction device. High-power compressors require multiple compression chambers, leading to large size, high cost, and high energy loss.

[0062] This hydraulic centrifugal compressor uses a potential energy receiving device to convert potential energy into rotational energy, which is then output to the main shaft of the centrifugal pump for energy reuse. This is because hydraulic motors can only utilize pressure energy; the kinetic potential energy of the liquid cannot be utilized, as it is lost before reaching the hydraulic motor. This reuse of potential energy adds kinetic energy for the next operation, causing the centrifugal pump to generate even greater kinetic potential energy. This potential energy is then received again by the receiving wheel, converted into rotational energy, and output to the main shaft of the centrifugal pump. Combined with the rotational energy of the electric motor, this generates even greater kinetic and pressure energy. This process continues indefinitely until the losses from high-speed operation become too high. Therefore, the simultaneous use of kinetic and pressure energy is far more energy-efficient than using only one type of energy. Current technologies typically use only one type of energy, resulting in significant energy waste.

[0063] It is important to note that the pressure energy consumed by the hydraulic chamber has little impact on the rotational energy provided by the external motor to the centrifugal pump. This is because the higher the flow rate and pressure consumed by the hydraulic chamber, the higher the required speed of the centrifugal pump, resulting in greater total power consumption. The greater the total power consumed by the centrifugal pump, the greater the potential energy of the liquid. After the potential energy is recovered by the receiving impeller, the rotational energy transferred to the centrifugal pump is also greater. Therefore, the power consumed by the hydraulic chamber is approximately proportional to the potential energy receiving device. Thus, the pressure energy consumed by the hydraulic chamber has little impact on the rotational energy provided by the external motor to the centrifugal pump. Specifically, a large energy consumption in the compression chamber will not significantly affect the energy consumption of the input motor; conversely, a small energy consumption in the compression chamber will not significantly affect the energy consumption of the input motor. When the flow rate is close to zero, the centrifugal pump impeller is almost idle, so the energy demand is also close to zero. However, the potential energy receiving device has no potential energy to receive. The centrifugal pump consumes the energy loss generated by the high-speed rotation of the impeller, but it can maintain a high output pressure. This is a difference from existing technologies.

[0064] The centrifugal force generated by this equipment is highly dependent on its rotational speed. Calculations using a centrifugal force calculator show that, within the material's tolerance range, higher rotational speeds generate greater centrifugal force, increasing incrementally. This results in greater energy savings. Increasing the rotational speed achieves both energy efficiency and reduced material usage. Higher rotational speeds also increase output power, allowing for a smaller equipment size, thus saving materials and minimizing resource consumption.

[0065] In summary, this invention provides a hydraulic centrifugal compressor, whose piston cylinder has a hydraulic chamber and a pneumatic chamber. The outlet and return port of the centrifugal pump are connected to the first and second flow channels of the hydraulic chamber through a reversing valve. The reversing valve changes the flow direction of the liquid. When the compressor starts, the main shaft drives the impeller to rotate. The liquid in the liquid chamber rotates at high speed under the action of the impeller, possessing kinetic and potential energy. The liquid passes through the outlet, enters the hydraulic chamber through the reversing valve, and drives the hydraulic piston to move. The hydraulic piston squeezes the liquid on the other side and returns it to the liquid chamber through the return port, forming a liquid circulation. At the same time, the liquid direction control switch controls the valve core of the reversing valve to move back and forth between the compression position and the recovery position, thereby driving the hydraulic piston to move back and forth and compress the gas in the pneumatic chamber. The movement of the hydraulic piston is driven by the liquid. The main shaft and impeller drive the liquid to flow at high speed, recovering and utilizing the potential energy of the high-speed flowing liquid to achieve energy saving.

[0066] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and substitutions can be made without departing from the technical principle of the present invention. For example, the centrifugal pump can be replaced with a conventional centrifugal pump, or the speed-increasing gear set can be replaced with a generator to convert the received kinetic energy into electrical energy and then drive the centrifugal pump to rotate through an electric motor. These improvements and substitutions should also be considered within the scope of protection of the present invention.

Claims

1. A hydraulic centrifugal compressor, characterized in that, The device includes a centrifugal pump, a potential energy receiving device, and a piston cylinder connected to the centrifugal pump. The centrifugal pump includes a pump casing, a main shaft rotatably mounted in the pump casing, and a vane anti-rotating mounted on the main shaft. The pump casing has a liquid-containing chamber for containing liquid. The potential energy receiving device includes an outer ring chamber that communicates with the liquid-containing cavity. A receiving wheel is rotatably mounted inside the outer ring chamber, and receiving blades are arranged on the receiving wheel. The pump casing has an outlet that communicates with the outer ring chamber and a return port that communicates with the liquid-containing cavity. The piston cylinder includes a hydraulic chamber, a pneumatic chamber, and a hydraulic piston, with one end of the hydraulic piston located in the hydraulic chamber and the other end located in the pneumatic chamber; The hydraulic chamber is provided with a first flow channel and a second flow channel. The first flow channel is arranged on the side of the hydraulic piston near the centrifugal pump, and the second flow channel is arranged on the side of the hydraulic piston near the pneumatic chamber. The hydraulic centrifugal compressor further includes a reversing valve, which includes a valve core movably arranged in the pump housing and a liquid direction control switch. The valve core has a compression position in its stroke where the liquid outlet communicates with the first flow channel and the liquid return port communicates with the second flow channel, and a recovery position where the liquid outlet communicates with the second flow channel and the liquid return port communicates with the first flow channel. The liquid direction control switch is used to control the movement direction of the reversing valve. The pump casing is also equipped with a speed-increasing gear set that meshes with the receiving wheel. The speed-increasing gear set is connected to the main shaft by a one-way gear meshing. The flap wheel has a hollow structure and a cavity that is separated from the liquid-containing chamber.

2. The hydraulic centrifugal compressor according to claim 1, characterized in that, The liquid direction control switch includes a valve stem arranged parallel to the valve core. A valve head is located at one end of the valve stem. Power flow channels are arranged at both axial ends of the valve core. The valve head has a reversing flow channel connecting the power flow channel to the outlet and return port for liquid-driven axial movement of the valve core. A first stop and a second stop extending into the hydraulic chamber are also arranged at the end of the valve stem away from the valve head. The first stop is located on the side of the hydraulic piston closer to the centrifugal pump, and the second stop is located on the side of the hydraulic piston closer to the pressure chamber. The hydraulic piston has an impact force during its stroke. The first stop member pushes the valve stem to a first limit position for axial movement and impacts the second stop member to push the valve stem to a second limit position for axial movement. When the hydraulic piston is in the first limit position, the outlet is connected to the first power flow channel of the valve core near the centrifugal pump end, and the return port is connected to the second power flow channel of the valve core near the hydraulic chamber end, so that the valve core moves to the compression position. When the hydraulic piston is in the first limit position, the outlet is connected to the second power flow channel of the valve core near the hydraulic chamber end, and the return port is connected to the first power flow channel of the valve core near the centrifugal pump end, so that the valve core moves to the recovery position.

3. The hydraulic centrifugal compressor according to claim 2, characterized in that, The valve stem has a through central shaft hole, and the valve stem has a radially extending connecting hole that communicates with the central shaft hole. The connecting hole is located at one end of the valve head near the hydraulic chamber.

4. The hydraulic centrifugal compressor according to claim 3, characterized in that, Both the first and second stop members are stop arms that are vertically arranged on the valve stem. The stop arms are L-shaped and arranged opposite to each other.

5. The hydraulic centrifugal compressor according to any one of claims 1-4, characterized in that, The liquid-containing chamber has an inner wall whose diameter gradually decreases along the direction from the centrifugal pump to the hydraulic chamber, and the constricted end of the inner wall is connected to the return port.

6. The hydraulic centrifugal compressor according to any one of claims 1-4, characterized in that, The blade wheel includes a main body and blades arranged at one axial end of the main body. Multiple blades are evenly distributed around the circumference of the main body, and the cavity is arranged on the main body.

7. The hydraulic centrifugal compressor according to claim 6, characterized in that, The inner wall of the flap wheel has a liquid channel extending along the axial direction of the flap wheel.

8. The hydraulic centrifugal compressor according to claim 7, characterized in that, There is a radial gap between the main body and the inner wall of the pump casing.

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