Radial-flow twin-pump motor cylinder and manufacturing process thereof

Abstract

The application discloses a radial flow distribution type combined pump motor cylinder and a manufacturing process thereof. The combined pump motor cylinder is mainly composed of a motor cylinder, a pump cylinder and a flow distribution cylinder. Required geometric structure elements are designed and processed on each cylinder. Each cylinder is welded into an integrated body through copper-based brazing. After welding, finishing is carried out. After nitriding heat treatment, each matching element is finely ground to obtain a finished product. The combined pump motor cylinder can be used for acceleration and deceleration transmission of machine-fluid hybrid transmission and pure mechanical transmission, and can be used for engine reverse towing deceleration braking force transmission. The combined pump motor cylinder has the advantages of compact structure, high integration, high hydraulic circuit transmission efficiency, small power loss, non-intervention of the hydraulic circuit in transmission during pure mechanical transmission, pure mechanical shaft transmission and high power transmission efficiency without hydraulic power loss.

Description

Technical Field

[0001] This invention relates to the field of mechanical-hydraulic hybrid transmission, and more particularly to a high-pressure energy-saving integrated pump motor cylinder and its manufacturing process for hybrid transmission of mechanical flow and closed hydraulic flow. Background Technology

[0002] The traditional integrated pump motor drive has the following existing technical problems: 1. The traditional integrated pump motor adopts a dual-shaft parallel structure design, with the motor cylinder and main shaft, pump cylinder and main shaft, variable cylinder and servo variable mechanism, and flow distribution mechanism all operating independently, resulting in low integration, complex mechanisms, and large size; 2. The traditional integrated pump motor itself can only perform single hydraulic fluid power transmission, and even when connected to a mechanical transmission at its output end, it can only achieve single series transmission; 3. The mechanical input power of the traditional mechanical-hydraulic mixed integrated pump motor can only be used as the transmission of the next higher stage, with torque transmitted downwards, making it impossible to achieve multi-path synchronous convergence transmission of torque; 4. The traditional integrated pump motor connected in series in the transmission system cannot be easily replaced to perform pure mechanical transmission. However, in actual working conditions, the host machine, which is running at a constant speed, does not require the intervention of hydraulic transmission, and pure mechanical transmission is sufficient to meet the needs. In this case, the intervention of hydraulic transmission will only bring power loss, and to achieve... The purely mechanical switching of traditional coupled pump motor drive systems requires complex switching and auxiliary transmission mechanisms. Continuous hydraulic intervention leads to high energy consumption and low efficiency of the main unit, resulting in insufficient energy saving. Furthermore, traditional coupled pump motor drives lack overspeed capabilities, failing to meet the needs of multiple operating conditions. Finally, the rated working pressure of traditional coupled pump motors is generally below 40MPa, with a maximum pressure not exceeding 50MPa, and the pressure rating cannot be further increased, failing to meet the needs of ultra-high pressure conditions. Given these existing technical deficiencies, a new transmission structure is urgently needed to solve the above problems. The coupled pump motor cylinder proposed in this invention can solve these issues, but its manufacturing presents significant technical challenges, requiring complex multi-stage heat treatment. To ensure final machining accuracy, heat treatment hardness, and welding quality, a complete and feasible manufacturing process and tooling are needed to solve the machining problems of this coupled pump motor cylinder. Summary of the Invention

[0003] The technical problem solved by the present invention is to provide a radial flow distribution type integrated pump motor cylinder and its manufacturing process, so as to solve the problems in the background art mentioned above.

[0004] The technical problem solved by this invention is achieved by the following technical solution:

[0005] The radial distribution type integrated pump motor cylinder body includes a motor cylinder, a pump cylinder, a distribution cylinder, motor welding copper foil, pump welding copper foil, motor positioning pin, and pump positioning pin. The welding end face of the motor cylinder is connected to the corresponding welding end face of the distribution cylinder and then fixed by welding with the motor welding copper foil. The welding end face of the pump cylinder is connected to the corresponding welding end face of the distribution cylinder and then fixed by welding with the pump welding copper foil. The motor positioning pin and the pump positioning pin play a circumferential positioning role during the welding process.

[0006] In this invention, the motor cylinder is mainly composed of a motor cylinder body, an internal spline, a motor positioning outer circle, a motor cylinder inner hole, a spline relief groove, a motor positioning pin hole, a motor cylinder outer circle, and a motor plunger insertion hole. The motor plunger insertion hole includes a motor plunger hole, a motor plunger stroke hole, and a motor flow channel hole.

[0007] The pump cylinder mainly consists of the pump cylinder body, pump positioning pin hole, oil replenishing cavity, pump positioning outer circle, pump cylinder outer circle, pump cylinder inner hole, pump balance hole, forward oil replenishing hole, reverse oil replenishing hole, forward overflow hole, reverse overflow hole, and pump plunger hole. The common parts of the forward and reverse oil replenishing holes include the oil replenishing radial flow channel hole, the oil replenishing disassembly cavity, the oil replenishing valve hole, the oil replenishing retaining ring groove, the oil replenishing outlet cavity, and the oil replenishing inlet cavity. The difference lies in that the forward oil replenishing hole also includes the oil replenishing flow channel hole, and the reverse oil replenishing hole also includes the flow... The oil replenishing valves in the inclined orifice, the forward oil replenishing port and the reverse oil replenishing port have the same structure and the oil replenishing opening direction is the same. The forward overflow port and the reverse overflow port have the same structure. Both include an overflow valve port, an overflow retaining ring groove, an overflow disassembly cavity, an overflow cavity, an overflow flow channel port and an inclined flow channel port. The overflow valves in the forward overflow port and the reverse overflow port have opposite overflow directions. The opening pressure of the valve in the forward overflow port is greater than the opening pressure of the valve in the reverse overflow port. The pump plunger port includes a pump plunger stroke port, a pump plunger port and a pump flow channel port.

[0008] The distribution cylinder is mainly composed of the distribution cylinder body, motor common pressure groove, distribution motor pin hole, common pressure flow channel, distribution pump pin hole, pump common pressure groove, distribution pump end boss, distribution pump oil passage hole, distribution pump radial valve hole, distribution motor radial valve hole, distribution motor oil passage hole, distribution motor end boss, distribution oil passage cavity, distribution cylinder outer ring, distribution cylinder inner ring, and distribution inner and outer support rings.

[0009] The motor welding copper foil includes an outer ring of motor copper foil, an inner ring of motor copper foil, a through hole in the inner ring of motor, an oil passage hole in the motor copper foil, a motor connecting bracket, and a pin hole in the motor copper foil.

[0010] The pump welding copper foil includes the pump copper foil outer ring, the pump copper foil inner ring, the pump inner ring through hole, the pump copper foil oil passage hole, the pump connecting bracket, and the pump copper foil pin hole.

[0011] In this invention, the outer ring and inner ring of the motor copper foil are coaxially arranged and fixedly connected by a motor connecting bracket. The inner ring of the motor copper foil has a through hole in the middle, and oil passage holes of the motor copper foil are evenly distributed around the rotation center of the inner ring of the motor copper foil. The outer ring of the motor copper foil has a pin hole. When the motor welding copper foil is attached to the welding surface of the distribution cylinder and the motor cylinder, the pin hole of the motor copper foil corresponds to the pin hole of the distribution motor, the oil passage holes of the motor copper foil correspond to the oil passage holes of the distribution motor, the outer ring of the motor copper foil corresponds to the outer ring of the distribution cylinder, the inner ring of the motor copper foil corresponds to the inner ring of the distribution cylinder, and the through hole of the inner ring of the motor corresponds to the inner hole formed by the boss at the end of the distribution motor.

[0012] The outer and inner rings of the pump copper foil are coaxially arranged and fixedly connected by a pump connecting bracket. The inner ring of the pump copper foil has a pump inner ring through hole in the middle, and pump copper foil oil passage holes are evenly distributed around the rotation center of the inner ring of the pump copper foil. The outer ring of the pump copper foil has a pump copper foil pin hole. When the pump welding copper foil is attached to the welding surface of the distribution cylinder and the pump cylinder, the pump copper foil pin hole corresponds to the distribution pump pin hole, the pump copper foil oil passage hole corresponds to the distribution pump oil passage hole, the outer ring of the pump copper foil corresponds to the outer ring of the distribution cylinder, the inner ring of the pump copper foil corresponds to the inner ring of the distribution cylinder, and the pump inner ring through hole corresponds to the inner hole formed by the boss at the end of the distribution pump.

[0013] In this invention, the motor cylinder body is a rotating body. The outer circle of the motor cylinder body is provided for mounting bearings. The outer circle of the motor cylinder body is also provided for positioning the motor. The outer circle of the motor cylinder and the outer circle of the motor positioning are connected to form the motor cylinder body. A motor positioning pin hole is provided along the axial direction on the main body of the motor positioning outer circle, and the motor positioning pin hole is located at the welded end of the motor cylinder. The non-welded end of the inner cavity of the motor cylinder body is provided with an internal spline for power transmission. A spline relief groove is provided in the middle of the inner cavity of the motor cylinder body, and the spline relief groove is located at one end of the internal spline. The welded end of the inner cavity of the motor cylinder body is provided with a motor cylinder inner hole for cooperating with the spindle. The rotation axis of the outer circle of the motor cylinder, the rotation axis of the outer circle of the motor positioning, the rotation axis of the internal spline, the rotation axis of the spline relief groove, and the rotation axis of the inner hole of the motor cylinder are coaxial.

[0014] On the main body of the motor cylinder, multiple motor plunger insertion holes are evenly distributed circumferentially with the rotation axis of the inner bore of the motor cylinder as the rotation center, and the rotation axis of the motor plunger insertion holes is parallel to the rotation axis of the inner bore of the motor cylinder. A motor plunger hole is provided at the upper part of the motor plunger insertion hole. A motor plunger stroke hole is provided in the main body of the motor cylinder at one end of the motor plunger hole. The inner diameter of the motor plunger stroke hole is larger than the inner diameter of the motor plunger hole. The motor plunger stroke hole is coaxial with the motor plunger hole. A motor flow channel hole is provided at the bottom of the motor plunger stroke hole. The motor flow channel hole is used to connect the motor plunger stroke hole and the distribution cylinder.

[0015] In this invention, the pump cylinder body is a rotating body. The outer circle of the pump cylinder body is provided for mounting bearings. The outer circle of the pump cylinder body is also provided for positioning the pump. The outer circle of the pump cylinder and the positioning the pump are connected to form the pump cylinder body. A positioning pin hole is provided along the axial direction on the main body of the positioning the pump. The positioning pin hole is located at the welded end of the pump cylinder. The inner cavity of the pump cylinder body is provided with a pump cylinder inner hole for cooperating with the main shaft. An oil filling cavity is provided in the middle of the inner cavity of the pump cylinder body. The inner diameter of the oil filling cavity is larger than the inner hole of the pump cylinder. The inner hole of the pump cylinder is divided into two parts by the oil filling cavity. The rotation axis of the outer circle of the pump cylinder, the rotation axis of the positioning the pump, the rotation axis of the oil filling cavity and the rotation axis of the inner hole of the pump cylinder are coaxial with each other.

[0016] On the pump cylinder body, multiple pump plunger insertion holes are evenly distributed around the rotation axis of the pump cylinder inner bore as the rotation center, and the rotation axis of the pump plunger insertion holes is parallel to the rotation axis of the pump cylinder inner bore. A pump plunger hole is provided at the upper part of the pump plunger insertion hole. A pump plunger stroke hole is provided in the pump cylinder body at one end of the pump plunger hole. The inner diameter of the pump plunger stroke hole is larger than the inner diameter of the pump plunger hole. The pump plunger stroke hole is coaxial with the pump plunger hole. A pump flow channel hole is provided at the bottom of the pump plunger stroke hole. The pump flow channel hole is used to connect the pump plunger stroke hole and the distribution cylinder.

[0017] The forward and reverse oil replenishment ports are alternately arranged between two adjacent pump plunger ports. From the non-welded end to the welded end of the pump cylinder body, the forward and reverse oil replenishment ports sequentially include an oil replenishment disassembly cavity, an oil replenishment retaining ring groove, an oil replenishment valve hole, an oil replenishment inlet chamber, an oil replenishment valve hole, and an oil replenishment outlet chamber. The oil replenishment valve hole is divided into two parts by the oil replenishment inlet chamber, and the inner diameter of the oil replenishment inlet chamber is larger than the inner diameter of the oil replenishment valve hole. When the oil replenishment valve is installed, the mating outer circle of the oil replenishment valve mates with the upper and lower parts of the oil replenishment valve hole, respectively. The system features a sealed fit. After the oil replenishing valve is installed, it is fixed and limited by a steel wire retainer ring located in the oil replenishing retainer ring groove. To remove the oil replenishing valve, first unscrew the open end of the steel wire retainer ring to the oil replenishing disassembly cavity, then use a tool to clamp the end of the steel wire retainer ring and remove it. The oil replenishing disassembly cavity facilitates the removal of the steel wire retainer ring. The oil replenishing radial flow channel hole extends radially from the outer circle of the pump cylinder through the oil replenishing inlet cavity until it connects with the oil replenishing cavity. During use, a bearing is installed on the outer circle of the pump cylinder, and the inner ring of the bearing connects the oil replenishing radial flow channel hole with the intersection point on the outer circle of the pump cylinder. The oil supply outlet of the forward oil supply port is sealed, and a flow channel oblique hole is provided between the oil supply outlet chamber and the inner bore of the pump cylinder. The bottom of the oil supply outlet chamber of the reverse oil supply port is provided with an oil supply flow channel hole. The oil supply outlet chamber of the reverse oil supply port is connected to the distribution cylinder through the oil supply flow channel hole. During use, a main shaft is installed inside the pump cylinder inner bore. The outer circumference of the main shaft is sealed to the upper and lower parts of the pump cylinder inner bore. Oil supply pressure flows into the oil supply cavity through the radial hole of the main shaft, and then flows into the oil supply inlet chamber through the radial flow channel hole. The oil supply inlet section is located in the oil supply inlet section. The oil replenishing valve sleeve is provided with an oil inlet channel, and the oil replenishing valve seat located in the oil replenishing outlet section is provided with an oil outlet channel. After the pressure oil enters the oil replenishing valve through the oil inlet channel, the valve core is opened and then flows out from the oil outlet channel of the oil replenishing valve into the oil replenishing outlet chamber. A distribution oil passage cavity is formed between the main shaft and the inner hole of the pump cylinder. The pressure oil of the oil replenishing outlet chamber of the positive oil replenishing insertion hole enters the distribution oil passage cavity through the inclined hole of the flow channel and is then delivered to the distribution cylinder. The pressure oil of the oil replenishing outlet chamber of the reverse oil replenishing insertion hole is delivered to the distribution cylinder through the oil replenishing flow channel hole.

[0018] Forward and reverse overflow ports are alternately arranged between two adjacent pump plunger ports. From the non-welded end to the welded end of the pump cylinder body, the forward and reverse overflow ports sequentially include an overflow disassembly cavity, an overflow retaining ring groove, an overflow valve port, an overflow cavity, an overflow flow channel port, and a replenishment / outlet chamber. An oblique flow channel hole is provided between the overflow cavity and the pump cylinder inner bore. The overflow valve port is divided into two parts by the overflow cavity, and the inner diameter of the overflow cavity is larger than the inner diameter of the overflow valve port. When overflow... When the valve is installed, the outer circumference of the relief valve seals with the upper and lower parts of the relief valve orifice. After installation, the relief valve is fixed and limited by a wire retaining ring located in the relief retaining ring groove. To remove the relief valve, first unscrew the open end of the wire retaining ring to the relief disassembly cavity, then use a tool to clamp the end of the wire retaining ring and remove it. The relief disassembly cavity facilitates the removal of the wire retaining ring. A high-pressure relief valve is installed in the forward relief port, and a low-pressure relief valve is installed in the reverse relief port. The low-pressure relief valve opens in the opposite direction. Relative to the high and low pressure during hydraulic deceleration, the high and low pressure oil circuits are reversed during engine reverse deceleration. High and low pressure relief valves are set to obtain different system relief pressures. A radial oil passage is provided on the relief valve sleeve located in the relief cavity section, and an end oil passage is provided at the end of the relief valve sleeve near the overflow passage hole. When the system overflows in the forward direction, pressurized oil from the distribution cylinder is delivered to the end of the relief valve sleeve through the overflow passage hole. The oil flows through the overflow valve opening core and then through the radial oil passage on the overflow valve sleeve to the overflow cavity, and then through the oblique hole of the flow passage to the distribution oil passage cavity. When the system overflows in reverse, the pressure oil from the distribution cylinder is transported through the distribution oil passage cavity to the oblique hole of the flow passage and then to the overflow cavity. The pressure oil flows through the radial oil passage on the overflow valve sleeve into the overflow valve opening core and then through the end oil passage of the overflow valve sleeve to the overflow flow passage hole and then to the distribution cylinder.

[0019] Pump balance holes are distributed circumferentially around the pump cylinder body. The rotation axis of the pump balance holes is parallel to the rotation axis of the pump cylinder inner bore. The pump balance holes are staggered between two adjacent pump plunger insertion holes.

[0020] The forward oil replenishment port, reverse oil replenishment port, forward overflow port, reverse overflow port, and pump balance port are independently and alternately arranged between two adjacent pump plunger ports.

[0021] In this invention, the main body of the distribution cylinder is a rotating body. The outer ring and inner ring of the distribution cylinder are connected as one unit by distribution inner and outer support rings. A motor common pressure groove and a pump common pressure groove are formed between the outer ring and the inner ring on both sides of the distribution inner and outer support rings. A common pressure flow channel is provided on the distribution inner and outer support rings to connect the motor common pressure groove and the pump common pressure groove. Radial valve holes for the distribution pump and radial valve holes for the distribution motor are respectively provided on both sides of the distribution inner and outer support rings along the radial direction, and the radial valve holes for the distribution pump and the distribution motor are evenly distributed circumferentially. Oil passage holes for the distribution pump and oil passage holes for the distribution motor are respectively provided on both sides of the distribution inner and outer support rings along the axial direction, and the oil passage holes for the distribution pump and the distribution motor are respectively located on the inner ring of the distribution cylinder. A distribution flow channel is provided inside the main body of the distribution cylinder. The oil-shaped cavity has a distribution pump end boss at one end and a distribution motor end boss at the other end. The inner diameter of the distribution cavity is larger than the inner diameter of the distribution pump end boss and the inner diameter of the distribution motor end boss, respectively. The rotation axis of the distribution cavity, the rotation axis of the distribution pump end boss, the rotation axis of the motor end boss, the circumferentially distributed rotation axis of the distribution pump oil passage hole, the circumferentially distributed rotation axis of the distribution motor oil passage hole, the rotation axis of the motor common pressure groove, the rotation axis of the pump common pressure groove, the rotation axis of the outer ring of the distribution cylinder, the rotation axis of the inner ring of the distribution cylinder, and the rotation axis of the inner and outer support rings of the distribution cylinder are coaxial with each other. A distribution motor pin hole is provided at one end of the outer ring of the distribution cylinder along the axial direction, and a distribution pump pin hole is provided at the other end of the outer ring of the distribution cylinder along the axial direction.

[0022] Oil distribution valves are respectively installed in the radial valve holes of the distribution pump and the radial valve holes of the distribution motor. The oil distribution valves are provided with mating bosses and grooves. By radially controlling the position of the oil distribution valves, the connection and closure of the oil passage hole of the distribution pump and the oil passage cavity of the distribution pump, the connection and closure of the oil passage hole of the distribution pump and the pump common pressure groove, the connection and closure of the oil passage hole of the distribution motor and the oil passage cavity of the distribution motor, and the connection and closure of the oil passage hole of the distribution motor and the motor common pressure groove are realized.

[0023] In this invention, when the motor cylinder is connected to the distribution cylinder, one end of the motor positioning pin is set in the motor positioning pin hole and the other end is set in the distribution motor pin hole. When the pump cylinder is connected to the distribution cylinder, one end of the pump positioning pin is set in the pump positioning pin hole and the other end is set in the distribution pump pin hole.

[0024] The pump flow channel hole is coaxially connected to the distribution pump oil passage hole, the motor flow channel hole is coaxially connected to the distribution motor oil passage hole, and the overflow flow channel hole and the replenishment flow channel hole are respectively connected to the pump common pressure groove.

[0025] In this invention, when the combined pump motor cylinder is installed in the main unit, it rotates under the drive of external power. Under the action of external pressure oil replenishment, the combined pump motor cylinder is filled with hydraulic oil. When the motor end swashplate tilts forward, the hydraulic circuit causes the combined pump motor cylinder to perform a deceleration transmission function. The pump end plunger, driven by the pump end swashplate, moves axially to force out the pressure oil in the plunger's stroke orifice. At this time, the corresponding distribution valve, under the control of an external mechanism, rotates along the radial valve orifice of the distribution pump towards the distribution cylinder's rotation center. Approaching and connecting the distribution pump oil passage hole and the pump common pressure groove, pressurized oil flows through the distribution pump oil passage hole and the pump common pressure groove, and then flows into the motor common pressure groove through the common pressure flow channel. Part of the distribution valves, located in the radial valve hole of the distribution motor, alternately connect the motor common pressure groove and the distribution motor oil passage hole under the control of an external mechanism. The pressurized oil in the motor common pressure groove flows into the motor plunger stroke hole through the distribution motor oil passage hole and the motor flow channel hole, thus pushing part of the plunger at the motor end to move axially. Under the action of the swashplate at the motor end, this part of the moving plunger circumferentially drives the motor cylinder and drives the output through the internal spline. The output shaft rotates to transmit power; this is the hydraulic drive output. Simultaneously, the pump-end plunger, under the action of the pump-end swashplate and sliding differential mechanism, performs analog oil pressure, driving the combined pump motor cylinder to perform circumferential mechanical motion. The pump-end plunger transmits power through the pump cylinder to the motor cylinder via the distribution cylinder, further driving the output shaft to rotate and transmit power. During this drive operation, another part of the motor-end plunger, under the action of the swashplate, returns, pressing the hydraulic oil sucked in during the previous extension work back into the motor plunger's stroke orifice. The distribution valve corresponding to this part of the plunger is controlled by an external mechanism. The distribution motor oil passage and motor common pressure groove are closed, and the distribution motor oil passage and distribution oil passage cavity are connected. This allows the hydraulic oil in the motor plunger stroke hole to enter the distribution oil passage cavity through the distribution motor oil passage. At the same time, another part of the distribution valve at the pump end is closed by the external mechanism, and the distribution pump oil passage and pump common pressure groove are closed, while the distribution pump oil passage and distribution oil passage cavity are connected. At this time, the pressure oil in the distribution oil passage cavity enters the pump plunger stroke hole through the distribution pump oil passage and pump flow passage hole, pushing the plunger at the pump end to return. This cycle is repeated to achieve continuously variable transmission of the machine-hydraulic mixture.

[0026] The continuously variable transmission (CVT) for hydraulic-mechanical mixing is achieved by adjusting the swashplate angle at the motor end. The speed at which the pump end plunger completes the suction and pressure of oil within a cycle is the analog speed. The flow rate at the motor end and the flow rate at the pump end are the same in the hydraulic circuit. That is, the product of the motor end displacement and the motor end output speed is equal to the product of the pump end displacement and the analog speed. The difference between the input speed of the external power at the pump end and the analog speed is the mechanical transmission speed. The mechanical transmission speed is the same as the motor end output speed. From this, the analog speed and output speed under different motor end displacements can be calculated.

[0027] When the amount of oil returning from the motor end to the distribution oil cavity is insufficient to meet the full return of the pump end plunger due to internal hydraulic leakage, external oil replenishment is activated. The replenished pressure oil is input through the radial hole of the main shaft, flows through the oil replenishment cavity, the oil replenishment radial flow channel hole on the positive oil replenishment port side, and the oil replenishment inlet chamber, and is output through the positive oil replenishment valve to the oil replenishment outlet chamber and the flow channel oblique hole on the positive oil replenishment port side, and then flows into the distribution oil cavity to replenish the pump end plunger, so that the return plunger of the pump end can fully return. The high pressure oil in the pump common pressure groove enters the corresponding oil replenishment outlet chamber through the oil replenishment flow channel hole on the reverse oil replenishment port side. Because the pressure of the high pressure oil is much higher than the replenishment pressure, the valve core of the oil replenishment valve on the reverse oil replenishment port side is closed under the action of pressure difference.

[0028] When the load pressure is higher than the set pressure of the high-pressure relief valve, the system opens the positive relief valve. At this time, the valve core of the low-pressure relief valve is closed under the combined action of the high-pressure oil and the replenishing oil.

[0029] In this invention, when the swashplate at the motor end is at zero, the hydraulic circuit does not intervene in the transmission, thus enabling the cylinder of the integrated pump motor to perform a purely mechanical constant speed transmission function. The piston at the motor end cannot move axially under the restriction of the swashplate at the motor end, and the piston at the pump end cannot move axially under the action of the circuit pressure oil. At this time, there is no relative sliding rotation between the swashplate, the external drive mechanism, and the piston. The analog transmission device has no hydraulic circuit for circumferential drive, and the circumferential drive is only a mechanical circuit. The external drive mechanism drives the piston at the pump end through the swashplate at the pump end, thereby driving the cylinder of the integrated pump motor and the main shaft to rotate and output power. That is, the analog speed is zero at this time, and the output speed of the motor end, the transmission speed of the mechanical circuit, and the input speed of the external power at the pump end are the same.

[0030] At this point, since the support between the pump-end plunger and the motor-end plunger is hydraulic oil, as the combined pump motor cylinder rotates, under the control of the distribution valve, the motor-end plunger alternately enters the high-pressure zone and then exits the high-pressure zone to enter the low-pressure zone. The plunger entering the low-pressure zone is pushed towards the motor-end swashplate by the replenishment pressure from the distribution oil cavity. During this high-low pressure alternation process, the hydraulic oil in the motor plunger stroke hole is replenished in time, thus ensuring the pressure build-up of the motor-end plunger relative to the pump-end plunger. At the same time, since there is no relative sliding rotation between the pump-end swashplate, the external drive mechanism, and the plunger, the distribution valve at the pump end has no radial movement relative to the pump cylinder during circumferential rotation. That is, the pump-end plunger does not have synchronous high-low pressure alternation relative to the motor end during circumferential movement. Consequently, the pump end cannot perform synchronous leakage replenishment relative to the motor end, while the replenishment at the motor end can only replenish its own leakage. Leakage at the pump end cannot be compensated. As the leakage increases, the pump end plunger is affected by the internal leakage of the system and produces axial movement. At this time, it is equivalent to the motor end swashplate producing a slight positive tilt. The internal leakage of the hydraulic circuit brings about the low-speed axial movement of the pump end plunger, which in turn causes the swashplate, together with the sliding drive mechanism and the plunger, to produce a relative circumferential differential speed movement. That is, analog speed is generated at this time. At this time, the operation mode of the pump end hydraulic circuit is the same as the operation mode of the motor end swashplate when it is tilted positively and decelerating. The pump end distribution valve follows and produces radial movement. The pump end plunger alternates between high and low pressure, so that the internal leakage of the pump end is effectively compensated. Therefore, when the motor end swashplate is at zero position, the mechanical circuit transmission is the main force and supplemented by the internal leakage speed difference transmission of the pump end hydraulic circuit. That is, when the motor end swashplate is at zero position, the output speed of the mechanical circuit transmission is lower than the input speed.

[0031] In this invention, when the swashplate at the motor end is tilted in the opposite direction, the hydraulic circuit causes the cylinder of the integrated pump motor to perform a speed-increasing transmission function. Because the analog speed of the pump-end plunger is zero when the swashplate at the motor end is at zero, the pump has lost its ability to pump high-pressure oil. At this time, the motor-end plunger, under the action of the tilting swashplate, performs high-pressure oil supply, and the functions of the pump and motor begin to switch. The motor produces the high-pressure oil pumping effect of the pump, while the pump, having lost its pumping ability, produces the output transmission effect of the motor under the action of the high-pressure oil from the motor end. Since the circumferential position of the swashplate at the motor end relative to the radial distribution mechanism at the motor end remains fixed, the high and low pressure areas at the motor end remain unchanged. Similarly, the high and low pressure areas at the pump end also maintain their original relative state. The high pressure pump oil area at the motor end delivers oil back to the high pressure oil area of ​​the pump. At this time, the rotation of the combined pump motor cylinder not only causes the motor end plunger to generate the counter-pressure at the zero position of the motor end swashplate on the hydraulic circuit, thus maintaining the original pure mechanical transmission, but also delivers the pressurized oil back to the pump end and drives the pump end plunger to extend outward along the axial direction, thereby causing the combined pump motor cylinder to generate a relatively faster speed than pure mechanical speed. Thus, the combined pump motor cylinder further increases its speed on the basis of the original pure mechanical transmission speed, and as the combined pump motor cylinder increases its speed, the acceleration of the combined pump motor cylinder shows an increasing trend.

[0032] During this process, the motor performs the function of the pump. The pump's analog speed is always zero, thus performing the motor's function. The operation mode of the high and low pressure relief valves and the forward and reverse oil replenishment valves is the same as the operation mode when the motor end swashplate is tilted forward for deceleration transmission.

[0033] In this invention, when the vehicle uses engine reverse drag to reduce speed, the swashplate at the motor end is in a forward tilt state, and the functions of the original pump and motor begin to switch. The high and low pressure in the combined pump motor cylinder reverses, and the combined pump motor cylinder continues to rotate in the original direction under the action of the vehicle's inertia. At this time, the plunger in the low-pressure area of ​​the motor end compresses the hydraulic oil in the motor plunger stroke hole under the combined action of the rotating combined pump motor cylinder and the swashplate at the motor end, and then enters the distribution oil passage cavity through the motor flow passage hole and the distribution motor oil passage hole. The pressurized oil entering the distribution oil passage cavity is then... The oil passage hole and pump flow passage hole of the distribution pump enter the pump plunger stroke hole in the low pressure zone, which in turn pushes the pump end plunger in this zone to extend outward. Under the action of the pump end swashplate, the pump end plunger generates a tendency to drive the cylinder of the combined pump motor to move in the opposite direction. At this time, the air pressure in the engine cylinder causes the cylinder of the combined pump motor to move in the opposite direction through the pump end swashplate. Through the driving force, the engine reverse drag speed reduction function is realized. Since the high and low pressure circuits are switched, the operation mode of the high and low pressure relief valves and the forward and reverse oil replenishment valves is opposite to the operation mode when the motor end swashplate is tilted forward to reduce speed.

[0034] When the amount of oil returning from the pump end to the distribution oil cavity is insufficient to meet the full return stroke requirement of the motor end plunger due to hydraulic internal leakage, external oil replenishment is activated. The replenished pressure oil is input through the radial hole of the main shaft, flows through the replenishment oil cavity, the replenishment oil radial flow channel hole on the reverse replenishment oil insertion hole side and the replenishment oil inlet chamber, and is output through the reverse replenishment oil valve to the replenishment oil outlet chamber and replenishment flow channel hole on the reverse replenishment oil insertion hole side, and then flows into the pump common pressure groove. Then, it replenishes the motor plunger stroke hole through the common pressure flow channel, the motor common pressure groove and the motor flow channel hole, so that the return plunger at the motor end can fully return. The high pressure oil in the distribution oil cavity enters the corresponding replenishment oil outlet chamber through the oblique hole of the flow channel on the forward replenishment oil insertion hole side. Because the pressure of the high pressure oil is much higher than the replenishment pressure, the valve core of the replenishment valve on the forward replenishment oil insertion hole side is closed under the action of pressure difference.

[0035] When the reverse load pressure is higher than the set pressure of the low-pressure relief valve, the system opens the reverse relief. At this time, the valve core of the high-pressure relief valve is closed under the combined action of the high-pressure oil and the replenishing oil.

[0036] The manufacturing process of the radial flow distribution type integrated pump motor cylinder body includes positioning fixtures, process structure, and process steps. The positioning fixtures include nuts, springs, upper positioning blocks, lower positioning blocks, tie rods, and bases. The process structure includes a cavitation profile, a thickness-fixed boss, and a positioning circle. The process steps are as follows:

[0037] Step 1: Normalizing the raw materials; the materials are steels suitable for nitriding treatment.

[0038] Step 2: Machining the shape and contour of the raw materials to obtain semi-finished products such as motor cylinders, pump cylinders, and distribution cylinders;

[0039] Step 3: Weld the semi-finished products of the motor cylinder, pump cylinder, and distribution cylinder from Step 2;

[0040] Step 4: Perform heat treatment on the combined pump motor cylinder body after welding in Step 3;

[0041] Step 5: Perform precision machining on the cylinder block of the integrated pump motor that has undergone heat treatment in Step 4;

[0042] Step Six: Nitride the cylinder block of the integrated pump motor that has undergone finishing in Step Five;

[0043] Step 7: Fine grind the cylinder block of the integrated pump motor that has undergone nitriding treatment in Step 6.

[0044] In this invention, during the processing of step two, due to the large deformation caused by the heat treatment after welding, machining allowances are left at the motor plunger hole, pump plunger hole, radial valve hole of the distribution motor, radial valve hole of the distribution pump, outer circle of the pump cylinder, outer circle of the motor cylinder, positioning annular end face of the motor positioning outer circle, and positioning annular end face of the pump positioning outer circle. This step completes the processing of the process structure. Only the bottom hole of the internal spline is machined, and the spline part is not machined, resulting in the machined semi-finished product in step two.

[0045] In this invention, during the welding in step three, the motor welding copper foil is placed between the motor cylinder and the distribution cylinder, and the pump welding copper foil is placed between the pump cylinder and the distribution cylinder. They are positioned by the process structure and the motor positioning pin and the pump positioning pin, respectively, and fixed by the positioning fixture.

[0046] The process structure has precipitating surfaces set at the intersection of the welding joint surface and the outer circle of each cylinder. After the cylinders are joined, a precipitating zone is formed to accommodate the copper precipitated from the high-temperature melting process. The welding quality is judged by observing the uniformity of the copper precipitated in the precipitating zone. A fixed-thickness boss is set at the welding joint surface between the inner hole of the pump cylinder and the welding joint surface, and a fixed-thickness boss is set at the welding joint surface between the inner hole of the motor cylinder and the welding joint surface. A positioning circle is set on the fixed-thickness boss, which is respectively positioned in conjunction with the distribution pump end boss and the distribution motor end boss of the distribution cylinder. After the cylinders are joined, the thickness of the copper foil before welding is greater than the thickness Q of the fixed-thickness boss, leaving a gap P. When the copper foil melts at high temperature, the gap P is eliminated under the action of the positioning fixture and the weight of the cylinder. The distance between the two welding joint surfaces is completely limited by the thickness of the fixed-thickness boss, which can ensure that the thickness of the copper after welding is controllable, and at the same time ensure the outflow of precipitated copper.

[0047] The tie rod of the positioning fixture axially penetrates the hollow inner cavity of the combined pump motor cylinder. One end of the tie rod is provided with an upper positioning block, and the other end is provided with a lower positioning block. Both ends of the tie rod are tightened by nuts. One side of the upper positioning block has a conical surface that contacts and engages with the conical surface of the pump cylinder or the motor cylinder. A spring is provided on the other side of the upper positioning block. The spring is fitted onto the tie rod and located between the nut and the upper positioning block. One side of the lower positioning block has a conical surface that contacts and engages with the conical surface of the pump cylinder or the motor cylinder. The other side of the lower positioning block is provided on the base. The nut is located in the inner cavity of the base. When the nuts at both ends are tightened, the spring is compressed to generate preload. During the welding process, the spring can adaptively adjust the dimensional changes caused by thermal expansion, i.e., eliminate the gap P.

[0048] The welding is done using copper-based brazing, with the copper foil being a copper-based filler metal, and the welding temperature is below 1200℃.

[0049] In this invention, the hardness of the tempering treatment in step four is greater than HRC25, and the quenching temperature is lower than 900℃.

[0050] In this invention, the finishing part in step five leaves a fine grinding allowance after nitriding treatment, the internal spline machining is completed in step five, and the removal of the process structure is completed in step five.

[0051] In this invention, the nitriding hardness in step six is ​​greater than HV700, the effective layer depth is greater than 0.2 mm, and the nitriding temperature is lower than 550°C.

[0052] In this invention, step 7 involves fine grinding of the portion of fine grinding allowance left in step 5.

[0053] In this invention, the manufacturing process is challenging due to the control of welding, heat treatment, and machining allowances at each stage. Improper welding temperature control can cause cracking at the weld. The weld thickness cannot be too thin or too thick, and uneven thickness is also unacceptable, as these factors directly affect the mechanical strength after welding. The post-weld tempering process is even more critical. The quenching and tempering processes must be properly coordinated to ensure that the tempering hardness is achieved while minimizing the impact of the quenching process on the weld. Improper quenching process control can cause porosity defects or even cracking at the weld. Improper control of machining allowances at each stage can lead to product scrap. Insufficient machining allowances will result in insufficient machining allowances due to deformation during welding and heat treatment, while excessive machining allowances will result in a large amount of material to be removed at the end. Since the nitriding hardened layer is relatively thin, with the high-hardness layer generally less than 0.1 mm, excessive material removal during final grinding will lead to a decrease in surface hardness or even complete loss of the high-hardness layer, ultimately causing the nitriding process to fail.

[0054] Beneficial effects:

[0055] 1. The integrated pump motor cylinder of the present invention realizes the integration of motor cylinder, pump cylinder and distribution cylinder into one unit. The cylinder is equipped with bidirectional overflow, bidirectional oil replenishment and bidirectional radial distribution, forming a highly integrated hydraulic closed transmission system. Moreover, the three cylinders are coaxially designed, and the integration degree is far higher than that of the existing dual-shaft parallel integrated pump motor.

[0056] 2. Traditional integrated pump motors can only transmit hydraulic fluid power in a single manner, and the subsequent mechanical transmission can only achieve series transmission. However, this invention can achieve parallel transmission of mechanical fluid power and hydraulic fluid power.

[0057] 3. In traditional mechanical-hydraulic hybrid pumps, the mechanical circuit of the motor only serves as the upper stage of transmission, and the torque transmission line is singular, which cannot achieve synchronous torque convergence and output. However, the parallel transmission of the present invention achieves speed division and torque convergence. When a large torque output operation is required, the hydraulic circuit reduces speed and increases torque. The mechanical circuit after the speed reduction is automatically matched and synchronized with the hydraulic circuit, realizing the convergence and coaxial synchronous output of hydraulic torque and mechanical torque.

[0058] 4. When the external host is running at a constant speed, there is no need to reduce speed and increase torque. At this time, only the mechanical torque is sufficient to overcome the running resistance. However, in traditional series-connected hydraulic-mechanical hybrid transmission, the hydraulic flow cannot be freely cut off under the existing conditions to achieve pure mechanical transmission. To achieve this, a complex switching and transmission mechanism needs to be set up separately. However, the integrated pump motor cylinder of this invention can achieve pure mechanical transmission by simply adjusting the tilt angle of the motor end swashplate. There is no need to set up a separate switching and transmission mechanism. Pure mechanical transmission effectively avoids the transmission efficiency problems caused by volume loss and mechanical friction loss due to hydraulic circuit intervention, which greatly improves the transmission efficiency of the whole machine, is highly efficient and energy-saving, and at the same time, effectively reduces transmission vibration and the resulting noise, achieving a stable operating effect.

[0059] 5. Without setting up an external mechanism, the present invention only needs to adjust the swashplate tilt angle at the motor end to obtain the overspeed function, that is, to obtain an output speed higher than the input speed to meet the needs of the host. Moreover, the overspeed of the present invention is hydraulic overspeed based on the original input speed, realizing torque-dividing speed-converging transmission, with no intermediate link loss and high transmission efficiency.

[0060] 6. The pump and motor functions of the present invention can be switched between each other according to the working conditions. That is, the motor can perform the function of the pump, and the pump can also perform the function of the motor. When using the engine to reverse drag to reduce speed, the present invention can continuously switch between normal driving and reverse drag to reduce speed. The system has no sudden operation and achieves a smooth operation effect when switching working conditions. Moreover, the pressure bearing capacity of the cylinder of the integrated pump and motor of the present invention in actual working conditions can exceed 100MPa, which is far greater than the maximum working pressure of the traditional integrated pump and motor.

[0061] 7. This invention solves the problem of the inability to process the internal flow channel geometry of the distribution cylinder by machining the three cylinders separately and then welding them together. Furthermore, the use of integral end-face hard brazing technology achieves reliable welding strength, meeting the mechanical performance requirements of the mechanical-hydraulic hybrid transmission. The reasonable control of welding, quenching, and nitriding temperatures in this invention effectively ensures the reliability of the finished product's welding quality while achieving the required final hardness and mechanical strength, thus avoiding welding defects such as porosity and cracks.

[0062] 8. The welding positioning fixture used in this invention can automatically adjust the relative position of the positioning according to the needs of thermal expansion and gap elimination, so as to meet the requirements of real-time changes in the axial dimensions of the three cylinders. The process structure set is removed in subsequent machining after positioning is completed, which not only completes the positioning function, but also does not affect the original structural design. The reasonable heat treatment process in this invention controls the deformation of each cylinder base, which not only completes the full contour machining of geometric elements, but also retains high surface hardness and hardness layer depth. Attached Figure Description

[0063] Figure 1This is a main sectional view of the integrated pump motor cylinder body according to a preferred embodiment of the present invention;

[0064] Figure 2 This is a main sectional view of the motor cylinder according to a preferred embodiment of the present invention;

[0065] Figure 3 This is a top view of the motor cylinder according to a preferred embodiment of the present invention;

[0066] Figure 4 This is a bottom view of the motor cylinder according to a preferred embodiment of the present invention;

[0067] Figure 5 This is a main sectional view of the distribution cylinder according to a preferred embodiment of the present invention;

[0068] Figure 6 This is a cross-sectional view of the flow distribution cylinder motor end AA of a preferred embodiment of the present invention;

[0069] Figure 7 This is a cross-sectional view of the distribution cylinder pump end distribution BB according to a preferred embodiment of the present invention;

[0070] Figure 8 This is a front rotating sectional view of the pump cylinder body CC according to a preferred embodiment of the present invention;

[0071] Figure 9 This is a rotatable sectional view of the pump cylinder body DD according to a preferred embodiment of the present invention;

[0072] Figure 10 This is a rotating sectional view of the pump cylinder body EE according to a preferred embodiment of the present invention;

[0073] Figure 11 This is a top view of the pump cylinder body according to a preferred embodiment of the present invention;

[0074] Figure 12 This is a schematic diagram of the motor welding copper foil according to a preferred embodiment of the present invention;

[0075] Figure 13 This is a schematic diagram of the pump welding copper foil according to a preferred embodiment of the present invention;

[0076] Figure 14 This is a schematic diagram of the spindle-fitting pressure chamber distribution in a preferred embodiment of the present invention;

[0077] Figure 15 This is a schematic diagram of welding positioning according to a preferred embodiment of the present invention;

[0078] Figure 16 This is a schematic diagram of welding assembly according to a preferred embodiment of the present invention. Detailed Implementation

[0079] To make the technical means, creative features, objectives and effects of this invention easier to understand, the invention will be further described below with reference to specific illustrations.

[0080] See Figures 1 to 14 The radial distribution type integrated pump motor cylinder body includes a motor cylinder 1, a pump cylinder 2, a distribution cylinder 3, a motor welding copper foil 4, a pump welding copper foil 5, a motor positioning pin 6, and a pump positioning pin 7. Its characteristic is that the welding end face of the motor cylinder 1 is connected to the corresponding welding end face of the distribution cylinder 3. The motor welding copper foil 4 is disposed between the welding end faces of the motor cylinder 1 and the distribution cylinder 3, thereby welding and fixing the motor cylinder 1 and the distribution cylinder 3 into a single unit via copper-based brazing. The welding end face of the pump cylinder 2 is connected to the corresponding welding end face of the distribution cylinder 3. The pump welding copper foil 5 is disposed between the welding end faces of the pump cylinder 2 and the distribution cylinder 3, thereby welding and fixing the pump cylinder 2 and the distribution cylinder 3 into a single unit via copper-based brazing. When the motor cylinder 1 and the distribution cylinder 3 are connected, they are circumferentially positioned by the motor positioning pin 6. When the pump cylinder 2 and the distribution cylinder 3 are connected, they are circumferentially positioned by the pump positioning pin 7.

[0081] In this embodiment, the motor cylinder 1 is mainly composed of a motor cylinder body 11, an inner spline 12, a motor positioning outer circle 15, a motor cylinder inner hole 17, a spline relief groove 18, a motor positioning pin hole 19, a motor cylinder outer circle 110, and a motor plunger insertion hole 1Z. The motor plunger insertion hole 1Z includes a motor plunger hole 13, a motor plunger stroke hole 14, and a motor flow channel hole 16.

[0082] The motor cylinder body 11 is a rotating body. An outer cylinder circle 110 for mounting bearings is provided around the outer periphery of the motor cylinder body 11. A motor positioning outer circle 15 is also provided around the outer periphery of the motor cylinder body 11. The outer cylinder circle 110 and the motor positioning outer circle 15 are connected to form the motor cylinder body 11. A motor positioning pin hole 19 is provided axially on the main body of the motor positioning outer circle 15, and the motor positioning pin hole 19 is located at the welded end of the motor cylinder 11. The non-welded end of the inner cavity of the motor cylinder body 11 is provided with… An internal spline 12 for power transmission is provided. A spline relief groove 18 is provided in the middle of the inner cavity of the motor cylinder body 11. The spline relief groove 18 is located at one end of the internal spline 12. The inner cavity of the motor cylinder body 11 is provided with a motor cylinder inner hole 17 for cooperating with the main shaft. The rotation axis of the outer circle 110 of the motor cylinder, the rotation axis of the outer circle 15 of the motor positioning, the rotation axis of the internal spline 12, the rotation axis of the spline relief groove 18 and the rotation axis of the inner hole 17 of the motor cylinder are coaxial.

[0083] On the motor cylinder body 11, a plurality of motor plunger insertion holes 1Z are evenly distributed circumferentially with the rotation axis of the inner bore 17 of the motor cylinder as the rotation center, and the rotation axis of the motor plunger insertion holes 1Z is parallel to the rotation axis of the inner bore 17 of the motor cylinder. A motor plunger hole 13 is provided at the upper part of the motor plunger insertion hole 1Z. A motor plunger stroke hole 14 is provided in the motor cylinder body 11 at one end of the motor plunger hole 13. The inner diameter of the motor plunger stroke hole 14 is larger than the inner diameter of the motor plunger hole 13. The motor plunger stroke hole 14 is coaxial with the motor plunger hole 13. A motor flow channel hole 16 is provided at the bottom of the motor plunger stroke hole 14. The motor flow channel hole 16 is used to connect the motor plunger stroke hole 14 and the distribution cylinder 3.

[0084] In this embodiment, the distribution cylinder 3 mainly consists of a distribution cylinder body 31, a motor common pressure groove 32, a distribution motor pin hole 33, a common pressure flow channel 34, a distribution pump pin hole 35, a pump common pressure groove 36, a distribution pump end boss 37, a distribution pump oil passage hole 38, a distribution pump radial valve hole 39, a distribution motor radial valve hole 310, a distribution motor oil passage hole 311, a distribution motor end boss 312, a distribution oil passage cavity 313, a distribution cylinder outer ring 314, a distribution cylinder inner ring 315, and distribution inner and outer support rings 316.

[0085] The main body 31 of the distribution cylinder is a rotating body. The outer ring 314 and the inner ring 315 of the distribution cylinder are connected as one unit by the inner and outer support rings 316. The outer ring 214 and the inner ring 315 of the distribution cylinder are located on both sides of the axial direction of the inner and outer support rings 316 to form a motor common pressure groove 32 and a pump common pressure groove 36. The inner and outer support rings 316 are provided with a common pressure flow channel 34 to connect the motor common pressure groove 32 and the pump common pressure groove 36. Radial valve holes 39 for the distribution pump and 310 for the distribution motor are respectively provided on both radial sides, and are evenly distributed circumferentially. On both sides of the radially symmetrical plane of the inner and outer support rings 316, axial oil passage holes 38 for the distribution pump and 311 for the distribution motor are respectively provided, and are located on the inner ring 315 of the distribution cylinder. The main body 31 of the distribution cylinder... A portion of the oil distribution cavity 313 is provided inside. One end of this portion of the oil distribution cavity 313 is provided with a distribution pump end boss 37, and the other end is provided with a distribution motor end boss 312. The inner diameter of the oil distribution cavity 313 is larger than the inner diameter of the distribution pump end boss 37 and the inner diameter of the distribution motor end boss 312, respectively. The rotation axis of the oil distribution cavity 313, the rotation axis of the distribution pump end boss 37, the rotation axis of the motor end boss 312, and the circumference of the distribution pump oil passage hole 38 are all related to this cavity. The circumferential distribution rotation axis of the distribution motor oil passage hole 311, the rotation axis of the motor common pressure groove 32, the rotation axis of the pump common pressure groove 36, the rotation axis of the distribution cylinder outer ring 314, the rotation axis of the distribution cylinder inner ring 315, and the rotation axis of the distribution inner and outer support rings 316 are coaxial with each other. One end of the distribution cylinder outer ring 314 is provided with a distribution motor pin hole 33 along the axial direction, and the other end of the distribution cylinder outer ring 314 is provided with a distribution pump pin hole 35 along the axial direction.

[0086] Oil distribution valves are respectively installed in the radial valve hole 39 of the distribution pump and the radial valve hole 310 of the distribution motor. The oil distribution valves are provided with mating bosses and grooves. By radially controlling the position of the oil distribution valves, the connection and closing of the oil passage hole 39 of the distribution pump and the oil passage cavity 313, the connection and closing of the oil passage hole 39 of the distribution pump and the pump common pressure groove 36, the connection and closing of the oil passage hole 311 of the distribution motor and the oil passage cavity 313, and the connection and closing of the oil passage hole 311 of the distribution motor and the motor common pressure groove 32 are realized.

[0087] In this embodiment, the pump cylinder 2 mainly consists of a pump cylinder body 21, a pump positioning pin hole 26, an oil replenishment cavity 29, a pump positioning outer circle 210, a pump cylinder outer circle 212, a pump cylinder inner hole 214, a pump balance hole 215, a forward oil replenishment hole 2M, a reverse oil replenishment hole 2N, a forward overflow hole 2U, a reverse overflow hole 2V, and a pump plunger hole 2X. The common parts of the forward oil replenishment hole 2M and the reverse oil replenishment hole 2N include an oil replenishment radial flow channel hole 216, an oil replenishment disassembly cavity 217, an oil replenishment valve hole 218, and an oil replenishment retaining ring. The groove 219, the oil replenishment outlet chamber 220, and the oil replenishment inlet chamber 221 are different in that the forward oil replenishment port 2M also includes an oil replenishment flow channel hole 222, and the reverse oil replenishment port 2N also includes a flow channel inclined hole 28; the forward overflow port 2U and the reverse overflow port 2V have the same structure, both of which include an overflow valve hole 22, an overflow retaining ring groove 23, an overflow disassembly cavity 24, an overflow cavity 25, an overflow flow channel hole 27, and a flow channel inclined hole 28; the pump plunger port 2X includes a pump plunger stroke hole 211, a pump plunger hole 213, and a pump flow channel hole 223.

[0088] The pump cylinder body 21 is a rotating body. The outer circle 212 of the pump cylinder body 21 is provided around the outer circle for mounting bearings. The outer circle 210 of the pump positioning is also provided around the outer circle of the pump cylinder body 21. The outer circle 212 and the outer circle 210 of the pump positioning are connected to form the pump cylinder body 21. A pump positioning pin hole 26 is provided along the axial direction on the main body of the outer circle 210 of the pump positioning, and the pump positioning pin hole 26 is located at the welded end of the pump cylinder 2. The inner cavity of the pump cylinder body 21 is provided with a pump cylinder inner hole 214 for cooperating with the main shaft. An oil filling cavity 29 is provided in the middle of the inner cavity of the pump cylinder body 21. The inner diameter of the oil filling cavity 29 is larger than that of the pump cylinder inner hole 214. The pump cylinder inner hole 214 is divided into two parts by the oil filling cavity 29. The rotation axis of the outer circle 212 of the pump cylinder, the rotation axis of the outer circle 210 of the pump positioning, the rotation axis of the oil filling cavity 29 and the rotation axis of the inner hole 214 of the pump cylinder are coaxial with each other.

[0089] On the pump cylinder body 21, a plurality of pump plunger insertion holes 2X are evenly distributed around the rotation axis of the pump cylinder inner hole 214 as the rotation center, and the rotation axis of the pump plunger insertion holes 2X is parallel to the rotation axis of the pump cylinder inner hole 214. A pump plunger hole 213 is provided at the upper part of the pump plunger insertion hole 2X. A pump plunger stroke hole 211 is provided in the pump cylinder body 21 at one end of the pump plunger hole 213. The inner diameter of the pump plunger stroke hole 211 is larger than the inner diameter of the pump plunger hole 213. The pump plunger stroke hole 211 is coaxial with the pump plunger hole 213. A pump flow channel hole 210 is provided at the bottom of the pump plunger stroke hole 211. The pump flow channel hole 210 is used to connect the pump plunger stroke hole 211 and the distribution cylinder 3.

[0090] The forward oil replenishment port 2M and the reverse oil replenishment port 2N are alternately arranged between two adjacent pump plunger ports 2X. From the non-welded end to the welded end of the pump cylinder body 21, the forward oil replenishment port 2M and the reverse oil replenishment port 2N are sequentially provided with an oil replenishment disassembly cavity 217, an oil replenishment retaining ring groove 219, an oil replenishment valve port 218, an oil replenishment inlet chamber 221, an oil replenishment valve port 218, and an oil replenishment outlet chamber 220. The oil replenishment valve port 218 is divided into two parts by the oil replenishment inlet chamber 221, and the inner diameter of the oil replenishment inlet chamber 221 is larger than the inner diameter of the oil replenishment valve port 218. When the oil replenishment valve is installed, the outer circle of the oil replenishment valve seals with the upper and lower parts of the oil replenishment valve port 218 respectively. After the oil replenishment valve is installed... The steel wire retainer ring is fixed and limited within the oil replenishment retainer ring groove 219. When removing the oil replenishment valve, first unscrew the open end of the steel wire retainer ring to the oil replenishment disassembly cavity 217, then use a tool to clamp the end of the steel wire retainer ring and remove it. The oil replenishment disassembly cavity 217 facilitates the disassembly of the steel wire retainer ring. The oil replenishment radial flow channel hole 216 extends radially from the outer circle 212 of the pump cylinder through the oil replenishment inlet cavity 221 until it connects with the oil replenishment cavity 29. During use, a bearing is installed on the outer circle 212 of the pump cylinder. The inner ring of the bearing seals the interface between the oil replenishment radial flow channel hole 216 and the outer circle 212 of the pump cylinder. A flow channel oblique hole 2 is provided between the oil replenishment outlet cavity 220 of the positive oil replenishment insertion hole 2M and the inner hole 214 of the pump cylinder. 8. The bottom of the oil supply outlet chamber 220 of the reverse oil supply port 2N is provided with an oil supply flow channel hole 222. The oil supply outlet chamber 220 of the reverse oil supply port 2N is connected to the distribution cylinder 3 through the oil supply flow channel hole 222. In use, a main shaft is installed in the inner hole 214 of the pump cylinder. The outer circle of the main shaft is sealed to the upper and lower parts of the inner hole 214 of the pump cylinder. The oil supply pressure oil is input into the oil supply cavity 29 through the radial hole of the main shaft, and then flows into the oil supply inlet chamber 221 through the oil supply radial flow channel hole 216. An oil inlet flow channel is provided on the oil supply valve sleeve located in the oil supply inlet chamber 221, and an oil outlet flow channel is provided on the oil supply valve seat located in the oil supply outlet chamber 220. The pressure oil passes through the oil supply valve... After the oil inlet channel enters the oil replenishing valve, the valve core opens and flows out from the oil outlet channel of the oil replenishing valve into the oil replenishing outlet chamber. The part between the main shaft and the lower part of the pump cylinder inner hole 214 forms another part of the distribution oil passage cavity 313. This part and a part on the distribution cylinder 3 form a complete distribution oil passage cavity 313. The pressure oil of the oil replenishing outlet cavity 220 of the forward oil replenishing port 2M enters the distribution oil passage cavity 313 through the flow channel inclined hole 28 and is then delivered to the distribution cylinder 3. The pressure oil of the oil replenishing outlet cavity 220 of the reverse oil replenishing port 2N is delivered to the distribution cylinder 3 through the oil replenishing flow channel hole 222. The oil replenishing valves set in the forward oil replenishing port 2M and the reverse oil replenishing port 2N have the same structure and the oil replenishing opening direction is the same.

[0091] The forward overflow port 2U and the reverse overflow port 2V are alternately arranged between two adjacent pump plunger ports 2X. From the non-welded end to the welded end of the pump cylinder body 21, the forward overflow port 2U and the reverse overflow port 2V are sequentially provided with an overflow disassembly cavity 24, an overflow retaining ring groove 23, an overflow valve port 22, an overflow cavity 25, an overflow flow channel port 22, and an overflow flow channel port 27. An oblique flow channel hole 28 is provided between the overflow cavity 25 and the pump cylinder inner bore 214. The overflow valve port 22 is divided into two parts by the overflow cavity 25, and the inner diameter of the overflow cavity 25 is larger than that of the overflow valve. The inner diameter of hole 22, when the overflow valve is installed, the outer diameter of the overflow valve is sealed with the upper and lower parts of the overflow valve hole 22 respectively. After the overflow valve is installed, it is fixed and limited by the wire retaining ring set in the overflow retaining ring groove 23. When removing the overflow valve, first unscrew the open end of the wire retaining ring to the overflow disassembly cavity 24, and then use a tool to clamp the end of the wire retaining ring and remove it. The overflow disassembly cavity 24 facilitates the disassembly of the wire retaining ring. A high-pressure overflow valve is installed in the positive overflow insertion hole 2U, and a low-pressure overflow valve is installed in the reverse overflow insertion hole 2V. The high-pressure overflow valve and the low-pressure overflow valve are... The overflow valves open in opposite directions. The opening pressure of the high-pressure overflow valve is greater than that of the low-pressure overflow valve. The high and low pressure oil circuits in the integrated pump motor cylinder are distributed relative to the hydraulic deceleration drive. The high and low pressure oil circuits are reversed during engine reverse drag deceleration. High and low pressure overflow valves are set to obtain different system overflow pressures. A radial oil passage is provided on the overflow valve sleeve located in the overflow cavity 25 section. An end oil passage is provided at the end of the overflow valve sleeve close to the overflow passage hole 27. When the system overflows in the forward direction, the pressure oil from the distribution cylinder 3 flows through the overflow passage hole 27. 7. The oil is supplied to the end passage of the relief valve sleeve and then enters the relief valve opening valve core. It flows out through the radial passage on the relief valve sleeve to the relief cavity 25 and then through the oblique hole 28 to the distribution oil passage cavity 313. When the system overflows in reverse, the pressure oil from the distribution cylinder 3 is supplied through the distribution oil passage cavity 313 to the oblique hole 28 and then to the relief cavity 25. The pressure oil flows into the relief valve opening valve core through the radial passage on the relief valve sleeve and is output through the end passage of the relief valve sleeve to the relief passage hole 27 and then to the distribution cylinder 3.

[0092] Pump balance holes 215 are distributed circumferentially on the pump cylinder body 21. The rotation axis of the pump balance holes 215 is parallel to the rotation axis of the pump cylinder inner hole 214. The pump balance holes 215 are staggered between two adjacent pump plunger insertion holes 2X.

[0093] The forward oil replenishment port 2M, the reverse oil replenishment port 2N, the forward overflow port 2U, the reverse overflow port 2V, and the pump balance port 215 are independently and alternately arranged between two adjacent pump plunger ports 2X.

[0094] In this embodiment, the motor welding copper foil 4 includes a motor copper foil outer ring 41, a motor connecting bracket 42, a motor copper foil pin hole 43, a motor copper foil inner ring 44, a motor copper foil oil passage hole 45, and a motor inner ring through hole 46.

[0095] The outer ring 41 and inner ring 44 of the motor copper foil are coaxially arranged and fixedly connected in the middle by the motor connecting bracket 42. The inner ring 44 of the motor copper foil has a motor inner ring through hole 46 in the middle. Motor copper foil oil passage holes 45 are evenly distributed around the rotation center of the inner ring 44 of the motor copper foil. The outer ring 41 of the motor copper foil has a motor copper foil pin hole 43. When the motor welding copper foil 4 is attached to the welding surface of the distribution cylinder 3 and the motor cylinder 1, the motor copper foil pin hole 43 corresponds to the distribution motor pin hole 33, the motor copper foil oil passage hole 45 corresponds to the distribution motor oil passage hole 311, the outer ring 41 of the motor copper foil corresponds to one side of the outer ring 314 of the distribution cylinder, the inner ring 44 of the motor copper foil corresponds to one side of the inner ring 315 of the distribution cylinder, and the inner ring through hole 46 of the motor corresponds to the inner hole formed by the end boss 312 of the distribution motor.

[0096] In this embodiment, the pump welding copper foil 5 includes a pump copper foil outer ring 51, a pump connecting frame 52, a pump copper foil pin hole 53, a pump copper foil inner ring 54, a pump copper foil oil passage hole 55, and a pump inner ring through hole 56.

[0097] The outer ring 51 and inner ring 54 of the pump copper foil are coaxially arranged and fixedly connected in the middle by the pump connecting bracket 52. The inner ring 54 of the pump copper foil has a pump inner ring through hole 56 in the middle. Pump copper foil oil passage holes 55 are evenly distributed around the rotation center of the inner ring 54 of the pump copper foil. The outer ring 51 of the pump copper foil has a pump copper foil pin hole 53. When the pump welding copper foil 5 is attached to the welding surface of the distribution cylinder 3 and the pump cylinder 2, the pump copper foil pin hole 53 corresponds to the distribution pump pin hole 35, the pump copper foil oil passage hole 55 corresponds to the distribution pump oil passage hole 38, the outer ring 51 of the pump copper foil corresponds to the other side of the outer ring 314 of the distribution cylinder, the inner ring 54 of the pump copper foil corresponds to the other side of the inner ring 315 of the distribution cylinder, and the pump inner ring through hole 56 corresponds to the inner hole formed by the distribution pump end boss 37.

[0098] In this embodiment, when the motor cylinder 1 is connected to the distribution cylinder 3, one end of the motor positioning pin 6 is set in the motor positioning pin hole 19 and the other end is set in the distribution motor pin hole 33. When the pump cylinder 2 is connected to the distribution cylinder 3, one end of the pump positioning pin 7 is set in the pump positioning pin hole 26 and the other end is set in the distribution pump pin hole 35.

[0099] Pump flow channel hole 223 is coaxially connected to distribution pump oil passage hole 38, motor flow channel hole 16 is coaxially connected to distribution motor oil passage hole 311, and overflow flow channel hole 27 and replenishment flow channel hole 222 are respectively connected to pump common pressure groove 36.

[0100] In this embodiment, when the combined pump motor cylinder is installed in the main unit, it rotates under the drive of external power. With the help of external pressure oil replenishment, the combined pump motor cylinder is filled with hydraulic oil. When the swashplate at the motor end tilts forward, the hydraulic circuit causes the combined pump motor cylinder to perform a reduction transmission function. The plunger at the pump end moves axially under the drive of the swashplate, forcing out the pressure oil in the plunger stroke hole 211. At this time, the distribution valve corresponding to this plunger, under the control of an external mechanism, moves along the radial valve hole 39 of the distribution pump towards the rotation center of the distribution cylinder 3, connecting the distribution pump oil passage hole 38 with the pump... The pressure oil flows through the common pressure groove 36, the distribution pump oil passage hole 38, and the pump common pressure groove 36, and then through the common pressure flow channel 34 into the motor common pressure groove 32. Part of the distribution valves, located in the radial valve hole 310 of the distribution motor, alternately connect the motor common pressure groove 32 and the distribution motor oil passage hole 311 under the control of an external mechanism. The pressure oil in the motor common pressure groove 32 flows through the distribution motor oil passage hole 311 and the motor flow channel hole 16 into the motor plunger stroke hole 14, thereby pushing part of the plunger at the motor end to move axially. Under the action of the swashplate at the motor end, this part of the running plunger circumferentially drives the motor cylinder 1 and drives the output shaft to rotate via the internal spline 12. Power is supplied via hydraulic drive. Simultaneously, the pump-end plunger, under the action of the pump-end swashplate and sliding differential mechanism, performs analog hydraulic drive while simultaneously driving the combined pump motor cylinder to perform circumferential mechanical motion. The pump-end plunger transmits power to the motor cylinder 1 via the pump cylinder 2 and the distribution cylinder 3, further driving the output shaft to rotate and transmit power. During this drive operation, another part of the motor-end plunger, under the action of the swashplate, returns, pressing the hydraulic oil sucked in during the previous extension work back to the motor plunger stroke hole 14. The corresponding distribution valve, under the control of an external mechanism, keeps the distribution motor oil passage hole 311 and the motor common pressure groove 32 in a position... In the closed state, the hydraulic oil in the distribution motor oil passage 311 and the distribution oil passage cavity 313 are connected, so that the hydraulic oil in the motor plunger stroke hole 14 enters the distribution oil passage cavity 313 through the distribution motor oil passage 311. At the same time, under the control of the external mechanism, the other part of the distribution valve at the pump end closes the distribution pump oil passage 38 and the pump common pressure groove 36, and then connects the distribution pump oil passage 38 and the distribution oil passage cavity 313. At this time, the pressure oil in the distribution oil passage cavity 313 enters the pump plunger stroke hole 211 through the distribution pump oil passage 38 and the pump flow passage hole 223 to push the plunger at the pump end to return. This cycle realizes the stepless speed change transmission of the machine-hydraulic mixture.

[0101] The continuously variable transmission (CVT) for hydraulic-mechanical mixing is achieved by adjusting the swashplate angle at the motor end. The speed at which the pump end plunger completes the suction and pressure of oil within a cycle is the analog speed. The flow rate at the motor end and the flow rate at the pump end are the same in the hydraulic circuit. That is, the product of the motor end displacement and the motor end output speed is equal to the product of the pump end displacement and the analog speed. The difference between the input speed of the external power at the pump end and the analog speed is the mechanical transmission speed. The mechanical transmission speed is the same as the motor end output speed. From this, the analog speed and output speed under different motor end displacements can be calculated.

[0102] When the amount of oil returning from the motor end to the distribution oil cavity 313 due to hydraulic internal leakage is insufficient to meet the full return of the pump end plunger, external oil replenishment is activated. The replenished pressure oil is input through the radial hole of the main shaft, flows through the replenishment oil cavity 29, the replenishment oil radial flow channel hole 216 on the positive replenishment oil insertion hole 2M side and the replenishment oil inlet chamber 221, and is output through the positive replenishment oil valve to the replenishment oil outlet chamber 220 on the positive replenishment oil insertion hole 2M side and the flow channel inclined hole 28, and then flows into the distribution oil cavity 313 to replenish the pump end plunger, so that the return plunger of the pump end is fully returned. The high pressure oil in the pump common pressure groove 36 enters the corresponding replenishment oil outlet chamber 220 through the replenishment oil flow channel hole 222 on the reverse replenishment oil insertion hole 2N side. Because the pressure of the high pressure oil is much higher than the replenishment pressure, the valve core of the replenishment valve on the reverse replenishment oil insertion hole 2N side is in the closed state under the action of pressure difference.

[0103] When the load pressure is higher than the set pressure of the high-pressure relief valve, the system opens the positive relief valve. At this time, the valve core of the low-pressure relief valve is closed under the combined action of the high-pressure oil and the replenishing oil.

[0104] In this embodiment, when the swashplate at the motor end is at zero, the hydraulic circuit does not intervene in the transmission, thus enabling the cylinder of the integrated pump motor to perform a purely mechanical constant speed transmission function. The piston at the motor end has no axial movement under the restriction of the swashplate at the motor end, and the piston at the pump end also has no axial movement under the action of the circuit pressure oil. At this time, there is no relative sliding rotation between the swashplate, the external drive mechanism, and the piston. The analog transmission device has no hydraulic circuit for circumferential drive, and the circumferential drive only has a mechanical circuit. The external drive mechanism drives the piston at the pump end through the swashplate at the pump end, thereby driving the cylinder of the integrated pump motor and the main shaft to rotate and output power. At this time, the analog speed is zero, and the output speed at the motor end, the transmission speed through the mechanical circuit of the integrated pump motor cylinder, and the input speed of the external power at the pump end are the same.

[0105] Since the support between the pump-end plunger and the motor-end plunger is hydraulic oil, as the combined pump motor cylinder rotates, under the control of the distribution valve, the motor-end plunger alternately enters the high-pressure zone and then exits the high-pressure zone to enter the low-pressure zone. The plunger entering the low-pressure zone is pushed towards the motor-end swashplate by the replenishment oil pressure from the distribution oil passage cavity 313. During this high-low pressure alternation process, the hydraulic oil in the motor plunger stroke hole 14 is replenished in time, thereby ensuring the pressure build-up of the motor-end plunger relative to the pump-end plunger. At the same time, since there is no relative sliding rotation between the pump-end swashplate, the external drive mechanism, and the plunger, the distribution valve at the pump end has no radial movement relative to the pump cylinder 2 during the circumferential rotation. That is, the pump-end plunger does not have synchronous high-low pressure alternation relative to the motor end during the circumferential movement, and therefore the pump end cannot perform synchronous leakage replenishment relative to the motor end. The replenishment oil at the motor end can only replenish the oil from its own oil. The leakage within the system cannot compensate for the leakage at the pump end. As the leakage increases, the pump end plunger undergoes axial movement due to the internal leakage of the system. This is equivalent to a slight positive tilt of the motor end swashplate. The internal leakage of the hydraulic circuit causes the axial movement of the pump end plunger, which in turn causes a relative circumferential differential speed movement between the swashplate, the sliding drive mechanism, and the plunger. This results in an analog speed. At this time, the operation mode of the pump end hydraulic circuit is consistent with the operation mode of the motor end swashplate when it is tilted positively and decelerating. The pump end distribution valve follows and generates radial movement. The pump end plunger alternates between high and low pressure, which effectively compensates for the internal leakage of the pump end. Therefore, when the motor end swashplate is at zero position, the mechanical circuit transmission is the main force, supplemented by the speed difference transmission due to the internal leakage of the pump end hydraulic circuit. That is, when the motor end swashplate is at zero position, the output speed of the mechanical circuit transmission is lower than the input speed.

[0106] In this embodiment, when the swashplate at the motor end is tilted in the opposite direction, the hydraulic circuit causes the cylinder of the integrated pump motor to perform a speed-increasing transmission function. Since the analog speed of the pump plunger is zero when the swashplate at the motor end is at zero, the pump has lost its ability to pump high-pressure oil. At this time, the motor plunger, under the action of the tilting swashplate, performs high-pressure oil supply, and the functions of the pump and motor begin to switch. The motor produces the high-pressure oil pumping effect of the pump, while the pump, having lost its pumping ability, produces the output transmission effect of the motor under the action of the high-pressure oil from the motor end. Because the circumferential position of the swashplate at the motor end relative to the radial distribution mechanism at the motor end remains fixed, the high and low pressure areas at the motor end maintain their original state. Similarly, the high and low pressure areas at the pump end also maintain their original relative state. The high-pressure pump oil area at the motor end delivers oil back to the high-pressure oil area of ​​the pump. At this time, the rotation of the combined pump motor cylinder not only causes the motor end plunger to generate the counter-pressure of the motor end swashplate at zero position on the hydraulic circuit, thus maintaining the original pure mechanical transmission, but also delivers the pressurized oil back to the pump end and drives the pump end plunger to extend outward along the axial direction, thereby causing the combined pump motor cylinder to generate a relatively faster speed relative to pure mechanical speed. Thus, the combined pump motor cylinder further increases its speed on the basis of the original pure mechanical transmission speed, and as the combined pump motor cylinder increases its speed, the acceleration of the combined pump motor cylinder shows an increasing trend.

[0107] During this process, the motor performs the function of the pump. The pump's analog speed is always zero, thus performing the motor's function. The operation mode of the high and low pressure relief valves and the forward and reverse oil replenishment valves is the same as the operation mode when the motor end swashplate is tilted forward for deceleration transmission.

[0108] In this embodiment, when the vehicle uses engine reverse drag to reduce speed, the swashplate at the motor end is in a forward tilt state, and the functions of the original pump and motor begin to switch. The high and low pressure regions in the integrated pump-motor cylinder are exchanged. Under the influence of the vehicle's inertia, the integrated pump-motor cylinder continues to rotate in its original direction. At this time, the plunger in the low-pressure region of the motor end compresses the hydraulic oil in the motor plunger stroke hole 14 under the combined action of the rotating integrated pump-motor cylinder and the motor end swashplate. This oil then enters the distribution oil passage cavity 313 through the motor flow passage hole 16 and the distribution motor oil passage hole 311. Pressurized oil enters the pump plunger stroke hole 211 in the low-pressure zone through the distribution pump oil passage hole 38 and the pump flow passage hole 223, thereby pushing the pump end plunger in this zone to extend outward. Under the action of the pump end swashplate, the pump end plunger generates a tendency to drive the cylinder of the combined pump motor to move in the opposite direction. At this time, the air pressure in the engine cylinder causes the cylinder of the combined pump motor to move in the opposite direction through the pump end swashplate. Through the driving force, the engine reverse drag speed reduction function is realized. Since the high and low pressure circuits are switched, the operation mode of the high and low pressure relief valves and the forward and reverse oil replenishment valves is opposite to the operation mode when the motor end swashplate is tilted forward to reduce speed.

[0109] When the amount of return oil from the pump end to the distribution oil cavity 313 is insufficient to meet the full return stroke requirement of the motor end plunger due to internal hydraulic leakage, external oil replenishment is activated. The replenished pressure oil is input through the radial hole of the main shaft, flows through the oil replenishment cavity 29, the oil replenishment radial flow channel hole 216 on the reverse oil replenishment port 2N side, and the oil replenishment inlet chamber 221, and is output through the reverse oil replenishment valve to the oil replenishment outlet chamber 220 and the oil replenishment flow channel hole 222 on the reverse oil replenishment port side 2N, and then flows into the pump co-pressure. The oil is fed into the motor plunger stroke hole 14 through the co-pressure flow channel 34, the motor co-pressure groove 32 and the motor flow channel hole 311, so that the return plunger at the motor end can fully return. The high-pressure oil flowing through the oil cavity 313 enters the corresponding oil supply outlet cavity 220 through the flow channel inclined hole 28 on the positive oil supply insertion hole 2M side. Because the pressure of the high-pressure oil is much higher than the oil supply pressure, the oil supply valve core on the positive oil supply insertion hole 2M side is in the closed state under the action of pressure difference.

[0110] When the reverse load pressure is higher than the set pressure of the low-pressure relief valve, the system opens the reverse relief. At this time, the valve core of the high-pressure relief valve is closed under the combined action of the high-pressure oil and the replenishing oil.

[0111] See Figures 15-16 The manufacturing process of the radial flow distribution type coupled pump motor cylinder body includes positioning fixture 8, process structure and process steps, the specific process steps are as follows:

[0112] Step 1: Normalizing the raw materials; the materials are steels suitable for nitriding treatment.

[0113] Step 2: Machining the shape and contour of the raw materials to obtain semi-finished products of motor cylinder 1, pump cylinder 2, and distribution cylinder 3;

[0114] Step 3: Weld the semi-finished products of motor cylinder 1, pump cylinder 2, and distribution cylinder 3 from Step 2;

[0115] Step 4: Perform heat treatment on the combined pump motor cylinder body after welding in Step 3;

[0116] Step 5: Perform precision machining on the cylinder block of the integrated pump motor that has undergone heat treatment in Step 4;

[0117] Step Six: Nitride the cylinder block of the integrated pump motor that has undergone finishing in Step Five;

[0118] Step 7: Fine grind the cylinder block of the integrated pump motor that has undergone nitriding treatment in Step 6.

[0119] In this embodiment, the machining allowance left at the following semi-finished products in step two—motor plunger hole 13, pump plunger hole 213, distribution motor radial valve hole 310, distribution pump radial valve hole 39, pump cylinder outer circle 212, motor cylinder outer circle 110, the positioning annular end face of motor positioning outer circle 15, and the positioning annular end face of pump positioning outer circle 210—is 0.3 mm thick. Step two completes the machining of the process structure. The internal spline only completes the bottom hole machining, and the spline part is not machined.

[0120] The process structure includes a sedimentation surface 11C, a thickness-fixed boss 11B, and a positioning circle 11D. The sedimentation surface 11C is respectively set at the intersection of the welding joint surface and the outer circle of each cylinder. After the cylinders are joined, a sedimentation zone is formed to accommodate the precipitated copper 4A flowing out at high temperature. The welding quality is judged by observing the uniformity of the precipitated copper 4A in the sedimentation zone. A thickness-fixed boss 11B is set at the welding joint surface between the inner hole 214 of the pump cylinder and the inner hole 17 of the motor cylinder. The thickness-fixed boss 11B is provided with... Positioning circle 11D is positioned in conjunction with the distribution pump end boss 37 and the distribution motor end boss 312 of the distribution cylinder 3. After the cylinders are docked, the thickness of the copper foil before welding is greater than the thickness Q of the fixed thickness boss 11B. There is a gap P between the fixed thickness boss 11B and the opposite welding surface. When the copper foil melts at high temperature, the gap P is eliminated under the action of the positioning fixture 8 and the cylinder's own weight. The distance between the two welding surfaces is limited by the thickness of the fixed thickness boss 11B, ensuring that the thickness of the copper after welding is controllable, thereby ensuring the outflow of precipitated copper 4A.

[0121] In this embodiment, in the welding of step three, the motor welding copper foil 4 is placed between the motor cylinder 1 and the distribution cylinder 3, and the pump welding copper foil 5 is placed between the pump cylinder 2 and the distribution cylinder 3. They are positioned by the process structure and the motor positioning pin 6 and the pump positioning pin 7, respectively, and fixed by the positioning fixture 8.

[0122] The positioning fixture 8 includes a pull rod 81, a nut 82, a spring 83, an upper positioning block 84, a lower positioning block 85, and a base 86. The pull rod 81 axially penetrates the hollow inner cavity of the combined pump motor cylinder. One end of the pull rod 81 is provided with the upper positioning block 84, and the other end is provided with the lower positioning block 85. The two ends of the pull rod 81 are tightened by the nut 82. One conical surface of the upper positioning block 84 contacts and engages with the conical surface of the pump cylinder 2 or the motor cylinder 1. The other side of the upper positioning block 84 is provided with the spring 83, which is fitted onto the pull rod 81 and located between the nut 82 and the upper positioning block 84. One conical surface of the lower positioning block 85 contacts and engages with the conical surface of the pump cylinder 2 or the motor cylinder 1. The other side of the lower positioning block 85 is provided on the base 86. The nut 82 is located in the inner cavity of the base 86. When the nuts 82 at both ends are tightened, the spring 83 is compressed to generate preload. During the welding process, the spring 83 can adaptively adjust the dimensional changes caused by thermal expansion and eliminate the gap P.

[0123] The welding is performed using copper-based brazing, with the copper foil being a copper-based filler metal, and the welding temperature being 1100–1150℃.

[0124] In this embodiment, the hardness of the tempering treatment in step four is HRC30-32, and the quenching temperature is 830-870℃.

[0125] In this embodiment, the finishing part in step five leaves a fine grinding allowance after nitriding treatment, the internal spline machining is completed in step five, and the removal of the process structure is completed in step five.

[0126] In this embodiment, the nitriding hardness in step six is ​​HV760~780, the effective layer depth is greater than 0.3mm, and the nitriding temperature is 450~500℃.

[0127] In this embodiment, step seven involves fine grinding the area with the fine grinding allowance left in step five.

[0128] In this embodiment, after completing the fine grinding process in step seven, the cylinder of the combined pump motor is demagnetized and subjected to anti-corrosion treatment.

[0129] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of the invention. Various changes and modifications can be made to the invention without departing from its spirit and scope, and all such changes and modifications fall within the scope of the present invention as claimed. The scope of protection of this invention is defined by the appended claims and their equivalents.

Claims

1. A radial-flux conjoined pump motor cylinder comprising a motor cylinder, a pump cylinder, a port cylinder, a motor soldered copper foil, a pump soldered copper foil, a motor dowel pin, and a pump dowel pin, characterized in that, The welding end face of the motor cylinder is connected to the corresponding welding end face of the distribution cylinder. The motor welding copper foil is placed between the welding end faces of the motor cylinder and the distribution cylinder. Then, the motor cylinder and the distribution cylinder are welded and fixed together by copper-based brazing. The welding end face of the pump cylinder is connected to the corresponding welding end face of the distribution cylinder. The pump welding copper foil is placed between the welding end faces of the pump cylinder and the distribution cylinder. Then, the pump cylinder and the distribution cylinder are welded and fixed together by copper-based brazing. When the motor cylinder and the distribution cylinder are connected, they are circumferentially positioned by the motor positioning pin. When the pump cylinder and the distribution cylinder are connected, they are circumferentially positioned by the pump positioning pin. The distribution cylinder mainly consists of a distribution cylinder body, a motor common pressure groove, a distribution motor pin hole, a common pressure flow channel, a distribution pump pin hole, a pump common pressure groove, a distribution pump end boss, a distribution pump oil passage hole, a distribution pump radial valve hole, a distribution motor radial valve hole, a distribution motor oil passage hole, a distribution motor end boss, a distribution oil passage cavity, a distribution cylinder outer ring, a distribution cylinder inner ring, and distribution inner and outer support rings. The distribution cylinder body is a rotating body. The outer ring and inner ring of the distribution cylinder are connected as one unit by the inner and outer support rings. A motor common pressure groove and a pump common pressure groove are formed between the outer ring and inner ring on both axial sides of the inner and outer support rings. Common pressure flow channels are provided on the inner and outer support rings to connect the motor common pressure groove and the pump common pressure groove. Radial valve holes for the distribution pump and the distribution motor are respectively provided on both radial sides of the inner and outer support rings. The radial valve holes for the distribution pump and the distribution motor are respectively arranged circumferentially. The distribution pump oil passage and the distribution motor oil passage are evenly distributed and located on both sides of the radially symmetrical plane where the inner and outer support rings of the distribution cylinder are located. The distribution pump oil passage and the distribution motor oil passage are located on the inner ring of the distribution cylinder. A part of the distribution oil passage cavity is provided inside the main body of the distribution cylinder. One end of the distribution oil passage cavity is provided with a distribution pump end boss and the other end is provided with a distribution motor end boss. The inner diameter of the distribution oil passage cavity is larger than the inner diameter of the distribution pump end boss and the inner diameter of the distribution motor end boss, respectively.

2. The radial-flowed siamese pump motor cylinder of claim 1, wherein, The motor cylinder mainly consists of a motor cylinder body, an internal spline, a motor positioning outer circle, a motor cylinder inner hole, a spline relief groove, a motor positioning pin hole, a motor cylinder outer circle, and a motor plunger insertion hole. The motor cylinder body is a rotating body. An outer circle for mounting bearings is provided around the motor cylinder body, and a motor positioning outer circle is also provided around the motor cylinder body. The outer circle and the motor positioning outer circle are connected to form the motor cylinder body. A motor positioning pin hole is provided axially on the motor positioning outer circle, and the motor positioning pin hole is located at the welded end of the motor cylinder. An internal spline for power transmission is provided at the non-welded end of the inner cavity of the motor cylinder body. A spline relief groove is provided in the middle of the inner cavity of the motor cylinder body, located at one end of the internal spline. An inner bore for cooperating with the spindle is provided at the welded end of the inner cavity of the motor cylinder body. The rotation axes of the outer circle, the motor positioning outer circle, the internal spline, the spline relief groove, and the inner bore are all coaxial.

3. The radial-flowed siamese pump motor cylinder of claim 2, wherein, The motor plunger insertion holes include a motor plunger hole, a motor plunger stroke hole, and a motor flow channel hole. These motor plunger insertion holes are evenly distributed circumferentially on the motor cylinder body with the rotation axis of the motor cylinder's inner bore as the center of rotation, and multiple motor plunger insertion holes are provided. The rotation axis of the motor plunger insertion holes is parallel to the rotation axis of the motor cylinder's inner bore. The upper part of each motor plunger insertion hole has a motor plunger hole. The motor plunger stroke hole is located within the motor cylinder body at one end of the motor plunger hole. The inner diameter of the motor plunger stroke hole is larger than the inner diameter of the motor plunger hole. The motor plunger stroke hole is coaxial with the motor plunger hole. The bottom of the motor plunger stroke hole has a motor flow channel hole, which connects to the motor plunger stroke hole and the distribution cylinder.

4. The radial-flowed siamese pump motor cylinder of claim 3, wherein, One end of the outer ring of the distribution cylinder is provided with a distribution motor pin hole along the axial direction, and the other end of the outer ring of the distribution cylinder is provided with a distribution pump pin hole along the axial direction. The rotation axes of the distribution oil cavity, the distribution pump end boss, the distribution motor end boss, the circumferentially distributed rotation axes of the distribution pump oil passage holes, the circumferentially distributed rotation axes of the distribution motor oil passage holes, the rotation axis of the motor common pressure groove, the rotation axis of the pump common pressure groove, the rotation axis of the distribution cylinder outer ring, the rotation axis of the distribution cylinder inner ring, and the rotation axes of the distribution inner and outer support rings are coaxial with each other. Oil distribution valves are respectively installed in the radial valve holes of the distribution pump and the radial valve holes of the distribution motor. The oil distribution valves are provided with mating bosses and grooves. By radially controlling the position of the oil distribution valves, the connection and closing of the oil passage hole of the distribution pump and the oil passage cavity of the distribution pump, the connection and closing of the oil passage hole of the distribution pump and the pump common pressure groove, the connection and closing of the oil passage hole of the distribution motor and the oil passage cavity of the distribution motor, and the connection and closing of the oil passage hole of the distribution motor and the motor common pressure groove are realized.

5. The radial-flowed siamese pump motor cylinder of claim 4, wherein, The pump cylinder mainly consists of a pump cylinder body, a pump positioning pin hole, an oil replenishing cavity, a pump positioning outer circle, a pump cylinder outer circle, a pump cylinder inner hole, a pump balance hole, a forward oil replenishing hole, a reverse oil replenishing hole, a forward overflow hole, a reverse overflow hole, and a pump plunger hole. The pump cylinder body is a rotating body. The outer circle of the pump cylinder body is provided for mounting bearings. The outer circle of the pump cylinder body is also provided for positioning the pump. The outer circle of the pump cylinder and the outer circle of the pump positioning are connected to form the pump cylinder body. The pump positioning pin hole is provided along the axial direction on the main body of the pump positioning outer circle, and the pump positioning pin hole is located at the welded end of the pump cylinder. The inner cavity of the pump cylinder body is provided with a pump cylinder inner hole for cooperating with the main shaft. The inner cavity of the pump cylinder body is provided with an oil filling cavity in the middle. The inner diameter of the oil filling cavity is larger than the inner hole of the pump cylinder. The inner hole of the pump cylinder is divided into two parts by the oil filling cavity. The rotation axis of the pump cylinder outer circle, the rotation axis of the pump positioning outer circle, the rotation axis of the oil filling cavity and the rotation axis of the pump cylinder inner hole are coaxial with each other. On the pump cylinder body, multiple pump plunger insertion holes are evenly distributed circumferentially with the rotation axis of the pump cylinder bore as the rotation center, and the rotation axis of the pump plunger insertion holes is parallel to the rotation axis of the pump cylinder bore. The forward oil replenishment hole and the reverse oil replenishment hole are alternately arranged between two adjacent pump plunger insertion holes, and the forward overflow hole and the reverse overflow hole are alternately arranged between two adjacent pump plunger insertion holes. Pump balance holes are distributed circumferentially on the pump cylinder body, and the rotation axis of the pump balance holes is parallel to the rotation axis of the pump cylinder bore. The pump balance holes are alternately arranged between two adjacent pump plunger insertion holes. The forward oil replenishment hole, the reverse oil replenishment hole, the forward overflow hole, the reverse overflow hole, and the pump balance hole are each independently and alternately arranged between two adjacent pump plunger insertion holes.

6. The radial flow distribution type combined pump motor cylinder body according to claim 5, characterized in that, The forward and reverse oil replenishing ports have the same parts, including an oil replenishing radial flow channel hole, an oil replenishing disassembly cavity, an oil replenishing valve hole, an oil replenishing retaining ring groove, an oil replenishing outlet cavity, and an oil replenishing inlet cavity. The difference is that the forward oil replenishing port also includes an oil replenishing flow channel hole, and the reverse oil replenishing port also includes a flow channel oblique hole. The forward and reverse overflow ports have the same structure, both including an overflow valve hole, an overflow retaining ring groove, an overflow disassembly cavity, an overflow cavity, an overflow flow channel hole, and a flow channel oblique hole. The pump plunger port includes a pump plunger stroke hole, a pump plunger hole, and a pump flow channel hole. The upper part of the pump plunger insertion hole is provided with a pump plunger hole, and the pump plunger stroke hole is provided in the pump cylinder body at one end of the pump plunger hole. The inner diameter of the pump plunger stroke hole is larger than the inner diameter of the pump plunger hole. The pump plunger stroke hole is coaxial with the pump plunger hole. The bottom of the pump plunger stroke hole is provided with a pump flow channel hole, which connects the pump plunger stroke hole and the distribution cylinder. The forward and reverse oil replenishing ports are sequentially provided with an oil replenishing disassembly cavity, an oil replenishing retaining ring groove, an oil replenishing valve hole, an oil replenishing inlet chamber, an oil replenishing valve hole, and an oil replenishing outlet chamber from the non-welded end to the welded end of the pump cylinder body. The oil replenishing valve hole is divided into two parts by the oil replenishing inlet chamber, and the inner diameter of the oil replenishing inlet chamber is larger than the inner diameter of the oil replenishing valve hole. When the oil replenishing valve is installed, the outer circle of the oil replenishing valve is sealed with the upper and lower parts of the oil replenishing valve hole respectively. After the oil replenishing valve is installed, it is fixed and limited by the steel wire retaining ring set in the oil replenishing retaining ring groove. When the oil replenishing valve is removed, the open end of the steel wire retaining ring is first screwed out to the oil replenishing disassembly cavity, and then the end of the steel wire retaining ring is clamped with a tool and removed. The oil replenishing radial flow channel hole extends radially from the outer circle of the pump cylinder through the oil replenishing inlet chamber until it connects with the oil replenishing cavity. During use, a bearing is installed on the outer circle of the pump cylinder. The inner ring of the bearing blocks the interface between the oil replenishing radial flow channel hole and the outer circle of the pump cylinder. A flow channel oblique hole is provided between the oil replenishing outlet chamber of the forward oil replenishing insertion hole and the inner hole of the pump cylinder. An oil replenishing flow channel hole is provided at the bottom of the oil replenishing outlet chamber of the reverse oil replenishing insertion hole. The oil replenishing outlet chamber of the reverse oil replenishing insertion hole is connected to the distribution cylinder through the oil replenishing flow channel hole. Another part of the distribution oil cavity is formed between the main shaft and the lower part of the inner hole of the pump cylinder. This part and a part on the distribution cylinder form a complete distribution oil cavity. The aforementioned positive overflow port and reverse overflow port are sequentially provided with an overflow disassembly cavity, an overflow retaining ring groove, an overflow valve hole, an overflow cavity, and an overflow flow channel hole from the non-welded end to the welded end of the pump cylinder body. An oblique flow channel hole is provided between the overflow cavity and the inner hole of the pump cylinder. The overflow valve hole is divided into two parts by the overflow cavity, and the inner diameter of the overflow cavity is larger than the inner diameter of the overflow valve hole. When the overflow valve is installed, the outer circle of the overflow valve is sealed with the upper and lower parts of the overflow valve hole respectively. After the overflow valve is installed, it is fixed and limited by the steel wire retaining ring set in the overflow retaining ring groove. When the overflow valve is removed, the open end of the steel wire retaining ring is first screwed out to the overflow disassembly cavity, and then the end of the steel wire retaining ring is clamped with a tool and removed.

7. The radial flow distribution type combined pump motor cylinder body according to claim 1, characterized in that, The motor welding copper foil includes an outer ring of motor copper foil, a motor connecting frame, a motor copper foil pin hole, an inner ring of motor copper foil, a motor copper foil oil passage hole, and a through hole in the inner ring of motor. The outer ring and the inner ring of motor copper foil are coaxially arranged and fixedly connected in the middle by the motor connecting frame. The inner ring of motor copper foil has a through hole in the middle. The oil passage holes of motor copper foil are evenly distributed around the rotation center of the inner ring of motor copper foil. The outer ring of motor copper foil has a pin hole. When the motor welding copper foil is attached to the welding surface of the distribution cylinder and the motor cylinder, the pin hole of motor copper foil corresponds to the pin hole of the distribution motor, the oil passage hole of motor copper foil corresponds to the oil passage hole of the distribution motor, the outer ring of motor copper foil corresponds to one side of the outer ring of the distribution cylinder, the inner ring of motor copper foil corresponds to one side of the inner ring of the distribution cylinder, and the through hole of the inner ring of motor corresponds to the inner hole formed by the boss at the end of the distribution motor. The pump welding copper foil includes an outer ring of pump copper foil, a pump connecting frame, a pump copper foil pin hole, an inner ring of pump copper foil, a pump copper foil oil passage hole, and a pump inner ring through hole. The outer ring and inner ring of pump copper foil are coaxially arranged and fixedly connected in the middle by the pump connecting frame. The pump inner ring has a pump inner ring through hole in the middle. Pump copper foil oil passage holes are evenly distributed around the rotation center of the inner ring of pump copper foil. The outer ring of pump copper foil has a pump copper foil pin hole. When the pump welding copper foil is attached to the welding surface of the distribution cylinder and the pump cylinder, the pump copper foil pin hole corresponds to the distribution pump pin hole, the pump copper foil oil passage hole corresponds to the distribution pump oil passage hole, the outer ring of pump copper foil corresponds to the other side of the outer ring of the distribution cylinder, the inner ring of pump copper foil corresponds to the other side of the inner ring of the distribution cylinder, and the pump inner ring through hole corresponds to the inner hole formed by the boss at the end of the distribution pump.

8. The radial flow distribution type combined pump motor cylinder body according to claim 6, characterized in that, When the motor cylinder is connected to the distribution cylinder, one end of the motor positioning pin is set in the motor positioning pin hole and the other end is set in the distribution motor pin hole. When the pump cylinder is connected to the distribution cylinder, one end of the pump positioning pin is set in the pump positioning pin hole and the other end is set in the distribution pump pin hole. The pump flow channel hole is coaxially connected to the distribution pump oil passage hole, the motor flow channel hole is coaxially connected to the distribution motor oil passage hole, and the overflow flow channel hole and the replenishment flow channel hole are respectively connected to the pump common pressure groove.

9. A transmission method for the cylinder body of a radially distributed coupled pump motor, used in the radially distributed coupled pump motor cylinder body as described in claim 6, characterized in that, When the integrated pump motor cylinder is in use, a main shaft is installed inside the pump cylinder bore. The outer circle of the main shaft is sealed to the upper and lower parts of the pump cylinder bore. The replenishing pressure oil is input into the replenishing cavity through the radial hole of the main shaft, and then flows into the replenishing inlet cavity through the replenishing radial flow channel hole. The replenishing valve sleeve located in the replenishing inlet cavity section is provided with an inlet flow channel, and the replenishing valve seat located in the replenishing outlet cavity section is provided with an outlet flow channel. After the pressure oil enters the replenishing valve through the inlet flow channel of the replenishing valve, the valve core is opened and then flows out from the outlet flow channel of the replenishing valve into the replenishing outlet cavity. The pressure oil in the replenishing outlet cavity of the forward replenishing port enters the distribution oil passage cavity through the inclined flow channel hole and is then delivered to the distribution cylinder. The pressure oil in the replenishing outlet cavity of the reverse replenishing port is delivered to the distribution cylinder through the replenishing flow channel hole. The replenishing valves in the forward and reverse replenishing ports have the same structure and the replenishing opening direction is the same. A high-pressure relief valve is installed in the forward overflow port, and a low-pressure relief valve is installed in the reverse overflow port. The high-pressure and low-pressure relief valves open in opposite directions, and the opening pressure of the high-pressure relief valve is greater than that of the low-pressure relief valve. The high and low pressure oil circuits in the integrated pump motor cylinder are distributed relative to the hydraulic deceleration drive. The high and low pressure oil circuits are reversed during engine reverse drag deceleration, and high and low pressure relief valves are installed to obtain different system overflow pressures. A radial oil passage is provided on the relief valve sleeve located in the overflow cavity section, and an end oil passage is provided at the end of the relief valve sleeve near the overflow passage hole. When the system overflows in the forward direction, the pressurized oil from the distribution cylinder is delivered through the overflow flow channel hole to the end oil passage of the overflow valve sleeve, and then enters the opening valve core of the overflow valve. It then flows out through the radial oil passage on the overflow valve sleeve to the overflow cavity, and then through the flow channel inclined hole to the distribution oil passage cavity. When the system overflows in the reverse direction, the pressurized oil from the distribution cylinder is delivered through the distribution oil passage cavity to the flow channel inclined hole, and then to the overflow cavity. The pressurized oil flows into the opening valve core of the overflow valve through the radial oil passage on the overflow valve sleeve, and then through the end oil passage of the overflow valve sleeve to the overflow flow channel hole, and then to the distribution cylinder.

10. The transmission method for the cylinder body of the radially distributed coupled pump motor according to claim 9, characterized in that, When the combined pump motor cylinder is installed in the main unit, the combined pump motor cylinder is in a rotating state under the drive of external power. Under the action of external pressure oil replenishment, the inside of the combined pump motor cylinder is filled with hydraulic oil. When the motor end swashplate tilts in the positive direction, the hydraulic circuit causes the combined pump motor cylinder to perform the deceleration transmission function. Driven by the swashplate at the pump end, the plunger at the pump end moves axially, forcing out the pressure oil in the plunger's stroke orifice. At this time, the corresponding distribution valve, under the control of an external mechanism, moves along the radial valve orifice of the distribution pump towards the rotation center of the distribution cylinder, connecting the distribution pump oil passage orifice with the pump common pressure groove. The pressure oil flows through the distribution pump oil passage orifice and the pump common pressure groove, and then through the common pressure flow channel into the motor common pressure groove. The distribution valves located in the radial valve orifice of the distribution motor, under the control of an external mechanism, alternately connect the motor common pressure groove and the distribution motor oil passage orifice. The pressure oil in the motor common pressure groove is then... The oil passage and flow passage of the motor flow motor flow into the stroke hole of the motor plunger, which in turn pushes part of the plunger at the motor end to move axially. Under the action of the swashplate at the motor end, the plunger in this part drives the motor cylinder circumferentially and drives the output shaft to rotate through the internal spline to transmit power. This is the hydraulic circuit drive output. At the same time, the plunger at the pump end, under the action of the swashplate at the pump end and the sliding differential mechanism, performs analog hydraulic oil drive and drives the cylinder body of the combined pump motor to perform circumferential mechanical movement. The plunger at the pump end transmits power through the pump cylinder to the motor cylinder through the distribution cylinder to further drive the output shaft to rotate and transmit power. During this drive operation, the other part of the plunger at the motor end, under the action of the swashplate, returns, pressing the hydraulic oil sucked in during the previous extension work back into the motor plunger stroke orifice. The corresponding plunger's distribution valve, under the control of an external mechanism, closes the distribution motor oil passage and the motor common pressure groove, and connects the distribution motor oil passage and the distribution oil passage cavity. This allows the hydraulic oil in the motor plunger stroke orifice to enter the distribution oil passage cavity through the distribution motor oil passage. Simultaneously, the other part of the distribution valve at the pump end, under the control of an external mechanism, closes the distribution pump oil passage and the pump common pressure groove, and then connects the distribution pump oil passage and the distribution oil passage cavity. At this time, the pressure oil in the distribution oil passage cavity flows through the distribution pump oil passage... The flow channel and pump flow channel holes enter the pump plunger stroke hole, pushing the plunger at the pump end to return. This cycle achieves continuously variable transmission of the hydraulic-mechanical mixture. The continuously variable transmission of the hydraulic-mechanical mixture is achieved by adjusting the swashplate angle at the motor end. The speed at which the pump end plunger completes the suction and pressure of the oil within the cycle is the analog speed. The flow rate at the motor end and the flow rate at the pump end in the hydraulic circuit are the same. That is, the product of the motor end displacement and the motor end output speed is equal to the product of the pump end displacement and the analog speed. The difference between the input speed of the external power at the pump end and the analog speed is the mechanical transmission speed. The mechanical transmission speed is the same as the output speed at the motor end. From this, the analog speed and output speed under different motor end displacements can be calculated. When hydraulic internal leakage causes insufficient return oil from the motor end to the distribution oil cavity to meet the full return of the pump end plunger, external oil replenishment is activated. The replenished pressure oil is input through the radial hole of the main shaft, flows through the replenishment oil cavity, the replenishment oil radial flow channel hole on the positive replenishment oil insertion hole side, and the replenishment oil inlet chamber, and is output through the positive replenishment oil valve to the replenishment oil outlet chamber and the flow channel oblique hole on the positive replenishment oil insertion hole side, and then flows into the distribution oil cavity to replenish the pump end plunger, so that the return plunger of the pump end can fully return. The high pressure oil in the pump common pressure groove enters the corresponding replenishment oil outlet chamber through the replenishment oil flow channel hole on the reverse replenishment oil insertion hole side. Because the pressure of the high pressure oil is much higher than the replenishment pressure, the valve core of the replenishment valve on the reverse replenishment oil insertion hole side is closed under the action of pressure difference. When the load pressure is higher than the set pressure of the high-pressure relief valve, the system opens the positive relief valve. At this time, the valve core of the low-pressure relief valve is closed under the combined action of the high-pressure oil and the replenishing oil.

11. The transmission method for the cylinder body of the radially distributed coupled pump motor according to claim 10, characterized in that, When the combined pump motor cylinder is installed in the main unit, and the swashplate at the motor end is at zero, the hydraulic circuit does not intervene in the transmission, thus allowing the combined pump motor cylinder to perform a purely mechanical constant speed transmission function. The piston at the motor end has no axial movement under the restriction of the swashplate at the motor end, and the piston at the pump end also has no axial movement under the action of the circuit pressure oil. At this time, there is no relative sliding rotation between the swashplate, the external drive mechanism, and the piston. The analog speed change device has no hydraulic circuit for circumferential drive, and the circumferential drive only has a mechanical circuit. The external drive mechanism drives the piston at the pump end through the swashplate at the pump end, thereby driving the combined pump motor cylinder and the main shaft to rotate and output power. At this time, the analog speed is zero, and the output speed at the motor end, the transmission speed through the mechanical circuit of the combined pump motor cylinder, and the input speed of the external power at the pump end are the same. Because the support between the pump-end plunger and the motor-end plunger is hydraulic oil, as the combined pump motor cylinder rotates, under the control of the distribution valve, the motor-end plunger alternately enters the high-pressure zone and then exits the high-pressure zone to enter the low-pressure zone. The plunger entering the low-pressure zone is pushed towards the motor-end swashplate by the replenishment oil pressure from the distribution oil cavity. During this high-low pressure alternation process, the hydraulic oil in the motor plunger stroke hole is replenished in time, thus ensuring the pressure build-up of the motor-end plunger relative to the pump-end plunger. At the same time, since there is no relative sliding rotation between the pump-end swashplate, the external drive mechanism, and the plunger, the distribution valve at the pump end has no radial movement relative to the pump cylinder during circumferential rotation. That is, the pump-end plunger does not have synchronous high-low pressure alternation relative to the motor end during circumferential movement. Therefore, the pump end cannot perform synchronous leakage replenishment relative to the motor end, while the motor end's replenishment can only replenish its own leakage. Leakage at the pump end cannot be compensated. As the leakage increases, the pump end plunger is affected by the internal leakage of the system and produces axial movement. At this time, it is equivalent to the motor end swashplate producing a slight positive tilt. The internal leakage of the hydraulic circuit causes the pump end plunger to move axially, which in turn causes the swashplate, together with the sliding drive mechanism and the plunger, to produce a relative circumferential differential speed movement. That is, analog speed is generated at this time. At this time, the operation mode of the pump end hydraulic circuit is the same as the operation mode of the motor end swashplate when it is tilted positively and decelerating. The pump end distribution valve follows and produces radial movement. The pump end plunger alternately replaces high and low pressure, so that the internal leakage of the pump end is effectively compensated. Therefore, when the motor end swashplate is at zero position, the mechanical circuit transmission is the main force and supplemented by the internal leakage speed difference transmission of the pump end hydraulic circuit. That is, when the motor end swashplate is at zero position, the output speed of the mechanical circuit transmission is lower than the input speed.

12. The transmission method for the cylinder body of the radially distributed combined pump motor according to claim 10, characterized in that, When the integrated pump motor cylinder is installed in the main unit, and the swashplate at the motor end is tilted in the opposite direction, the hydraulic circuit causes the integrated pump motor cylinder to perform a speed-increasing transmission function. Since the analog speed of the pump end plunger is zero when the swashplate at the motor end is at zero, the pump has lost its high-pressure pumping capability. At this time, the motor end plunger, under the action of the tilting swashplate, performs high-pressure oil supply, and the functions of the pump and motor begin to switch. The motor produces the high-pressure pumping effect of the pump, while the pump, having lost its pumping capability, produces the output transmission effect of the motor under the action of the high-pressure oil supply at the motor end. Because the circumferential position of the swashplate at the motor end relative to the radial distribution mechanism at the motor end remains fixed, the high and low pressure areas at the motor end remain... The original state remains unchanged. Similarly, the high and low pressure areas at the pump end also maintain their original relative state. The high-pressure pump oil area at the motor end delivers oil back to the high-pressure oil area of ​​the pump. At this time, the rotation of the combined pump motor cylinder not only causes the piston at the motor end to generate the counter-pressure at the zero position of the swashplate at the motor end on the hydraulic circuit, thus maintaining the original pure mechanical transmission, but also delivers the pressurized oil back to the pump end and drives the piston at the pump end to extend outward along the axial direction, thereby causing the combined pump motor cylinder to generate a relatively faster speed relative to pure mechanical speed. Thus, the combined pump motor cylinder further increases its speed on the basis of the original pure mechanical transmission speed, and as the combined pump motor cylinder increases its speed, the acceleration of the combined pump motor cylinder shows an increasing trend. During this process, the motor performs the function of the pump. The pump's analog speed is always zero, thus performing the motor's function. The operation mode of the high and low pressure relief valves and the forward and reverse oil replenishment valves is the same as the operation mode when the motor end swashplate is tilted forward for deceleration transmission.

13. The transmission method for the cylinder body of the radially distributed coupled pump motor according to claim 10, characterized in that, When the integrated pump-motor cylinder is installed in the main unit, and the vehicle uses engine braking to reduce speed, the swashplate at the motor end is in a forward tilt state. The functions of the original pump and motor begin to switch, and the high and low pressure areas in the integrated pump-motor cylinder are exchanged. Under the action of the vehicle's inertia, the integrated pump-motor cylinder continues to rotate in the original direction. At this time, the plunger in the low-pressure area of ​​the motor end compresses the hydraulic oil in the motor plunger stroke hole under the combined action of the rotating integrated pump-motor cylinder and the swashplate at the motor end. This oil then enters the distribution oil passage cavity through the motor flow passage hole and the distribution motor oil passage hole, and enters the distribution oil passage cavity. The pressure oil in the cavity enters the pump plunger stroke hole in the low-pressure zone through the distribution pump oil passage hole and the pump flow passage hole, thereby pushing the pump end plunger in this zone to extend outward. Under the action of the pump end swashplate, the pump end plunger generates a tendency to drive the cylinder of the combined pump motor to move in the opposite direction. At this time, the air pressure in the engine cylinder causes the cylinder of the combined pump motor to move in the opposite direction through the pump end swashplate. Through the driving force, the engine reverse drag speed reduction function is realized. Since the high and low pressure circuits are switched, the operation mode of the high and low pressure relief valves and the forward and reverse oil replenishment valves is opposite to the operation mode when the motor end swashplate is tilted forward to reduce speed. When the amount of oil returning from the pump end to the distribution oil cavity is insufficient to meet the full return stroke requirement of the motor end plunger due to hydraulic internal leakage, external oil replenishment is activated. The replenished pressure oil is input through the radial hole of the main shaft, flows through the replenishment oil cavity, the replenishment oil radial flow channel hole on the reverse replenishment oil insertion hole side and the replenishment oil inlet chamber, and is output through the reverse replenishment oil valve to the replenishment oil outlet chamber and replenishment flow channel hole on the reverse replenishment oil insertion hole side, and then flows into the pump common pressure groove. Then, it replenishes the motor plunger stroke hole through the common pressure flow channel, the motor common pressure groove and the motor flow channel hole, so that the return plunger at the motor end can fully return. The high pressure oil in the distribution oil cavity enters the corresponding replenishment oil outlet chamber through the oblique hole of the flow channel on the forward replenishment oil insertion hole side. Because the pressure of the high pressure oil is much higher than the replenishment pressure, the valve core of the replenishment valve on the forward replenishment oil insertion hole side is closed under the action of pressure difference. When the reverse load pressure is higher than the set pressure of the low-pressure relief valve, the system opens the reverse relief. At this time, the valve core of the high-pressure relief valve is closed under the combined action of the high-pressure oil and the replenishing oil.

14. A manufacturing process for a radially distributed integrated pump motor cylinder body, used in the radially distributed integrated pump motor cylinder body as described in claim 6, comprising positioning fixtures, process structure, and process steps, characterized in that, The specific process steps are as follows: Step 1: Normalizing the raw materials; the materials are steels suitable for nitriding treatment. Step 2: Machining the shape and contour of the raw materials to obtain semi-finished products such as motor cylinders, pump cylinders, and distribution cylinders; Step 3: Weld the semi-finished products of the motor cylinder, pump cylinder, and distribution cylinder from Step 2; Step 4: Perform heat treatment on the combined pump motor cylinder body after welding in Step 3; Step 5: Perform precision machining on the cylinder block of the integrated pump motor that has undergone heat treatment in Step 4; Step Six: Nitride the cylinder block of the integrated pump motor that has undergone finishing in Step Five; Step 7: Fine grind the cylinder block of the integrated pump motor that has undergone nitriding treatment in Step 6.

15. The manufacturing process of the radial flow distribution type combined pump motor cylinder body according to claim 14, characterized in that, The semi-finished products machined in step two have a machining allowance equal to the wall thickness at the motor plunger hole, pump plunger hole, radial valve hole of distribution motor, radial valve hole of distribution pump, outer circle of pump cylinder, outer circle of motor cylinder, locating annular end face of motor positioning outer circle, and locating annular end face of pump positioning outer circle. The machining of the process structure is completed in step two. Only the bottom hole of the internal spline is machined, and the spline part is not machined. The process structure includes a diaphragm surface, a thickness-fixed boss, and a positioning circle. The diaphragm surface is set at the intersection of the welding joint surface and the outer circle of each cylinder. After the cylinders are joined, a diaphragm zone is formed. A thickness-fixed boss is set at the welding joint surface of the pump cylinder inner hole and at the welding joint surface of the motor cylinder inner hole. A positioning circle is set on the thickness-fixed boss. The positioning circle cooperates with the distribution pump end boss and the distribution motor end boss of the distribution cylinder for positioning. After the cylinders are joined, the thickness of the copper foil before welding is greater than the thickness Q of the thickness-fixed boss. A gap P is left between the thickness-fixed boss and the opposite welding surface. When the copper foil melts at high temperature, the gap P is eliminated under the action of the positioning fixture and the cylinder's own weight. The distance between the two welding joint surfaces is limited by the thickness of the thickness-fixed boss.

16. The manufacturing process of the radial flow distribution type combined pump motor cylinder body according to claim 15, characterized in that, In step three, the welding of the motor welding copper foil is placed between the motor cylinder and the distribution cylinder, and the welding of the pump welding copper foil is placed between the pump cylinder and the distribution cylinder. They are positioned by the process structure and the motor positioning pin and the pump positioning pin, respectively, and fixed by the positioning fixture. The positioning fixture includes a pull rod, a nut, a spring, an upper positioning block, a lower positioning block, and a base. The pull rod axially penetrates the hollow inner cavity of the integrated pump motor cylinder. One end of the pull rod is equipped with an upper positioning block, and the other end is equipped with a lower positioning block. The two ends of the pull rod are tightened by nuts. One conical surface of the upper positioning block contacts and engages with the conical surface of the pump cylinder or the motor cylinder. A spring is installed on the other side of the upper positioning block. The spring is fitted onto the pull rod and located between the nut and the upper positioning block. One conical surface of the lower positioning block contacts and engages with the conical surface of the pump cylinder or the motor cylinder. The other side of the lower positioning block is located on the base. The nut is located in the inner cavity of the base. When the nuts at both ends are tightened, the spring is compressed to generate preload. During the welding process, the spring can adaptively adjust the dimensional changes caused by thermal expansion and eliminate the gap P. The welding is performed using copper-based brazing, with the copper foil being a copper-based filler metal, and the welding temperature is below 1200℃.

17. The manufacturing process of the radial flow distribution type combined pump motor cylinder body according to claim 14, characterized in that, In step four, the hardness of the quenching and tempering treatment is greater than HRC25, and the quenching temperature is lower than 900℃. The finishing part in step five leaves a fine grinding allowance after nitriding treatment. The internal spline machining is completed in step five, and the removal of the process structure is completed in step five. In step six, the nitriding hardness is greater than HV700, the effective layer depth is greater than 0.2 mm, and the nitriding temperature is lower than 550℃. Step seven involves fine grinding the area that was left with the fine grinding allowance in step five. After completing the precision grinding process in step seven, the cylinder block of the integrated pump motor is demagnetized and subjected to anti-corrosion treatment.

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