Hybrid hydraulic drive housing and method of manufacturing

Abstract

The application discloses a drive housing for mechanical-hydraulic parallel transmission and a manufacturing method thereof. The drive housing adopts a swash plate biasing self-rotation structure, realizes differential rotation for speed change transmission through self-rotation, and then realizes power split into mechanical flow and hydraulic flow, realizes adaptive speed matching, and then realizes power aggregation and parallel output transmission after speed change. The finishing machining of the housing adopts a positioning principle of mutual reference and accessories are dynamically balanced with the housing to ensure dynamic balance of the housing after installation.

Description

Technical Field

[0001] This invention relates to the field of mechanical-hydraulic hybrid transmission, and more particularly to a drive housing for hybrid transmission of mechanical flow and closed hydraulic flow, and a method for manufacturing the same. Background Technology

[0002] Traditional mechanical-hydraulic hybrid transmissions combine power in series, but cannot combine mechanical and hydraulic power in parallel. This results in complex structures and low transmission efficiency in existing mechanical-hydraulic hybrid transmissions. The key technical challenge in parallel transmission of mechanical and hydraulic power lies in how to integrate these two power flows. More specifically, it is about designing a transmission component that can receive external power and synchronously split the received power into mechanical and hydraulic flows in real time. Furthermore, the mechanical and hydraulic flows can be adaptively speed-matched, then re-aggregated, and finally output in parallel after speed change.

[0003] Given the existing technical deficiencies, there is an urgent need to propose a new transmission structure to solve the problems of the existing technical deficiencies. The mechanical-hydraulic hybrid drive housing proposed in this invention can solve the problems of the existing technology, but it has great technical difficulties in manufacturing. It needs to face the problem of controlling the machining accuracy of complex multi-process and multiple clamping. To ensure the final machining accuracy and transmission mechanical performance, a complete and feasible manufacturing method is needed to solve the machining accuracy control problem of the mechanical-hydraulic hybrid drive housing. Summary of the Invention

[0004] The technical problem solved by the present invention is to provide an organic-hydraulic mixing drive housing and its manufacturing method, so as to solve the problems in the background art mentioned above.

[0005] The technical problem solved by this invention is achieved by the following technical solution:

[0006] The geometric elements set on the hydraulic-mechanical mixing drive housing include the main shaft bearing cavity, housing input end face, outer bearing support circle, bearing gear ring transition outer circle, gear ring transmission outer circle, bearing outer circle, bearing left end face, transition arc, thrust surface, cylinder bearing outer circle, eccentric outer circle, cylinder bearing cavity, cylinder bearing transition cavity, eccentric inner cavity, housing output end face, drive bearing retaining ring, drive bearing cavity, housing outer conical surface, bearing right end face, transmission pin hole, transition end face, main shaft through hole, flushing inner cavity, fastening screw hole, left oblique cutting surface, left cutting surface, lower cutting surface, right cutting surface, right oblique cutting surface, oblique conical surface, drive transition cavity, and the center line C, left view right deflection rotation line E, inclined axis T and included angle K formed by the geometric elements. The center line C is parallel to the left view right deflection rotation line E, and the center line C intersects the inclined axis T at an angle K to form a plane. This plane is perpendicular to the deviation of the right deflection rotation line E from the center line C.

[0007] The outer periphery of the drive housing, from the input end face to the output end face, is sequentially provided with an outer bearing support circle, a bearing gear ring transition outer circle, a gear ring drive outer circle, a load-bearing outer circle, a housing outer conical surface, a cylinder load-bearing outer circle, and an eccentric outer circle. The outer bearing support circle, the bearing gear ring transition outer circle, the gear ring drive outer circle, the load-bearing outer circle, the housing outer conical surface, and the cylinder load-bearing outer circle are coaxial about the center line C. The rotation axis of the eccentric outer circle is the right-biased rotation line E in the left view.

[0008] The drive housing cavity is provided with the following components sequentially from the output end face to the input end face: an eccentric inner cavity, a cylinder bearing transition cavity, a cylinder bearing cavity, a drive transition cavity, a drive bearing retaining ring, a drive bearing cavity, a flushing inner cavity, a spindle through hole, and a spindle bearing cavity. The rotation axis of the eccentric inner cavity is the right-biased rotation line E in the left view. The eccentric inner cavity is coaxial with the eccentric outer circle and its rotation axis is the right-biased rotation line E in the left view. The cylinder bearing transition cavity, cylinder bearing cavity, spindle through hole, and spindle bearing cavity are coaxial and their rotation axis is the center line C. The drive transition cavity, drive bearing retaining ring, drive bearing cavity, and flushing inner cavity are coaxial and their rotation axis is the inclined axis T.

[0009] Due to the offset of the drive bearing retaining ring, drive bearing cavity, flushing cavity, drive transition cavity, and transmission pin hole, the center of gravity of the drive housing before dynamic balancing cutting is not on the center line C. It is necessary to cut and remove the material on the outside of the drive housing to achieve dynamic balance and reduce weight, thereby reducing rotational inertia. The material removed from the outside of the drive housing after cutting forms a left oblique cutting surface, a left cutting surface, a lower cutting surface, a right cutting surface, and a right oblique cutting surface. In order to facilitate balance adjustment, the main material of the cylinder bearing transition cavity corresponding to the eccentric direction is further cut to form an oblique conical surface.

[0010] In this invention, the outer bearing support circle is smaller than the bearing gear ring transition outer circle, and a thrust surface is formed between the outer bearing support circle and the bearing gear ring transition outer circle. The bearing gear ring transition outer circle is smaller than the gear ring drive outer circle, and a transition end face is formed between the bearing gear ring transition outer circle and the gear ring drive outer circle. The gear ring drive outer circle is smaller than the load-bearing outer circle, and a load-bearing right end face is formed between the gear ring drive outer circle and the load-bearing outer circle. A drive pin hole and a fastening screw hole are provided on the load-bearing right end face side. The drive pin hole and the fastening screw hole are located between the gear ring drive outer circle and the load-bearing outer circle and transmit power through the gear ring drive outer circle. The rotation axes of the moving pin hole and the fastening screw hole are perpendicular to the right end face of the bearing. The half-cone angle of the outer conical surface of the housing is consistent with the included angle K. The diameter of the large circle end of the outer conical surface of the housing is smaller than the diameter of the outer circle of the bearing. The diameter of the small circle end of the outer conical surface of the housing is smaller than the diameter of the outer circle of the cylinder bearing. The left end face of the bearing is connected to the large circle end of the outer conical surface of the housing through a transition arc. The small circle end of the outer conical surface of the housing is connected to the outer circle of the cylinder bearing through multiple continuous intersecting transition arcs. The outer circle of the cylinder bearing is smaller than the eccentric outer circle. The outer circle of the cylinder bearing and the eccentric outer circle are connected through a transition arc.

[0011] In this invention, the cylinder bearing transition cavity is larger than the cylinder bearing cavity, the eccentric inner cavity is larger than the cylinder bearing transition cavity, a thrust surface is formed between the eccentric inner cavity and the cylinder bearing transition cavity, a tool relief groove is provided at the intersection of the eccentric inner cavity and the thrust surface, a thrust surface is formed between the drive transition cavity and the cylinder bearing cavity, the drive bearing cavity is larger than the drive transition cavity, and a drive bearing retaining ring is provided between the drive bearing cavity and the drive transition cavity, the flushing inner cavity is smaller than the drive bearing cavity, a thrust surface is formed between the flushing inner cavity and the drive bearing cavity, the spindle through hole penetrates the drive housing, one end of the spindle through hole is connected to the flushing inner cavity and the other end is connected to the spindle bearing cavity, a thrust surface is formed between the spindle through hole and the spindle bearing cavity, and the housing output end face, housing input end face, bearing left end face, bearing right end face, and transition end face are perpendicular to the center line C.

[0012] In this invention, during the driving operation, the drive housing is provided with bearings in the cylinder bearing cavity, drive bearing cavity, main shaft bearing cavity, and outer bearing support circle. The inner ring of the bearing in the cylinder bearing cavity is installed on the piston cylinder body, and the inner ring of the bearing in the main shaft bearing cavity is installed on the main shaft. The main shaft and the piston cylinder body are coaxially fixed. The outer ring of the bearing in the outer bearing support circle is installed on the housing. The bearings in the cylinder bearing cavity, main shaft bearing cavity, and outer bearing support circle complete the positioning and load-bearing transmission of the drive housing. The drive housing can only rotate around the center line C. The main shaft passes through the main shaft through hole and the main shaft bearing cavity, and the end face of the piston cylinder body extends into the drive transition cavity.

[0013] In this invention, a transmission gear is provided on the outer circle of the gear ring drive, and a pin set in the transmission pin hole is also set on the transmission gear to limit the circumferential position of the transmission gear relative to the drive housing. A screw passes through the transmission gear and is screwed into the fastening screw hole to fasten the transmission gear to the drive housing. The power source drives the drive housing to rotate through the transmission gear.

[0014] In this invention, an eccentric ring is provided inside the eccentric cavity, and the eccentric cavity drives and controls the flow distribution valve through the eccentric ring. The thrust surface restricts the axial position of the eccentric ring on one side.

[0015] In this invention, one side of the outer ring of the bearing installed in the cylinder bearing cavity contacts and limits the thrust surface, the cylinder bearing transition cavity facilitates the installation of the bearing into the cylinder bearing cavity, one side of the outer ring of the bearing installed in the main shaft bearing cavity contacts and limits the thrust surface, the inner ring of the bearing on the outer bearing support circle contacts and limits the thrust surface, one side of the outer ring of the bearing in the drive bearing cavity contacts and limits the thrust surface, and the other side is limited by a retaining ring provided in the drive bearing retaining ring.

[0016] In this invention, a drive swashplate is provided on the inner ring of the bearing in the drive bearing cavity. The drive housing drives the plunger on the plunger cylinder through the drive swashplate. A radial oil outlet is provided on the main shaft in the main shaft through hole. Part of the oil entering the main shaft through hole flows into the housing through the main shaft bearing cavity, and the other part flows back to the housing through the flushing inner cavity, drive bearing cavity, drive transition cavity, cylinder bearing cavity, cylinder bearing transition cavity, and eccentric inner cavity, thereby lubricating and cooling the bearing.

[0017] See Figures 1-14 The manufacturing method of the organic-hydraulic mixing drive housing includes the following specific steps:

[0018] Step 1: Perform quenching and tempering heat treatment on the drive housing blank;

[0019] Step 2: Perform the first machining on the geometric elements designed for the drive housing, with some geometric elements having machining allowances;

[0020] Step 3: Perform surface heat treatment on the drive housing after the first machining process;

[0021] Step 4: Perform finishing on the drive housing after surface heat treatment;

[0022] Step 5: Perform dynamic balancing on the finished drive housing.

[0023] In this invention, the blank material in step one is alloy steel with a tempering hardness greater than HRC20.

[0024] In this invention, the machining of the drive housing in step two is completed in one setup using a turning-boring-milling composite machining center to ensure the positional accuracy between the various parts.

[0025] In step two, the blank holding the input end face of the housing is machined for the first time. First, all the geometric contours of the inner cavity are machined, then the outer contours are machined, and finally it is cut off from the input end face of the housing.

[0026] The geometric elements with machining allowances in the first machining process mentioned in step two include: spindle bearing cavity, outer bearing support circle, bearing gear ring transition outer circle, gear ring drive outer circle, cylinder bearing cavity, eccentric inner cavity, drive bearing cavity, thrust surface, and bearing right end face.

[0027] In this invention, the surface heat treatment in step three is nitriding, the nitriding layer depth is greater than 0.3 mm, and the nitriding hardness is greater than HV700.

[0028] In this invention, the finishing process in step four involves first using a hard-cutting machine tool to clamp the outer circle of the cylinder bearing and using the left end face of the bearing as the axial positioning end face. After completing the positioning and clamping, the spindle bearing cavity, thrust surface, outer bearing support circle, gear ring drive outer circle, bearing right end face, and bearing gear ring transition outer circle are hard-cut. After completing the above finishing process, a second clamping is performed. The bearing gear ring transition outer circle is clamped using a hard-cutting machine tool and the right end face of the bearing is used as the axial positioning end face. Then, the circumferential position of the drive housing is restricted by the transmission pin hole. After completing the positioning and clamping, the eccentric inner cavity, thrust surface, cylinder bearing cavity, and drive bearing cavity are hard-cut.

[0029] In this embodiment, during the dynamic balancing calibration in step five, components that rotate with the drive housing are installed on the drive housing, and the spindle bearing cavity and cylinder bearing cavity are used as positioning references for dynamic balancing calibration. Beneficial effects

[0030] The mechanical-hydraulic mixing drive housing of the present invention receives external power through a transmission gear on the drive housing, and drives the swashplate driven plunger mounted on the bearing through the drive bearing cavity and the bearing. Because the inclined axis T of the drive bearing cavity forms an angle K with the center line C of the drive housing driven by the power source, the swashplate can rotate around the inclined axis T while revolving around the center line C. The rotation of the swashplate causes a speed difference between the revolution speed of the cylinder plunger and the revolution speed of the drive housing, that is, a variable speed rotation effect is produced. The revolution speed of the cylinder plunger driven by the swashplate rotation is mechanical flow transmission after power splitting after the revolution speed is reduced. The revolution speed difference generated by the swashplate rotation is converted into hydraulic flow transmission to drive the piston oil speed. The revolution speed of the pump oil output by the motor is consistent with the revolution speed of the cylinder plunger, thereby realizing the transmission effect of parallel mechanical flow transmission and hydraulic flow transmission and aggregated output. In this process, the speed difference is established by the displacement ratio of the pump and the motor. As the ratio of the two changes, the speed difference is adaptively adjusted, thereby realizing the transmission effect of adaptive matching of the revolution speed of mechanical flow and hydraulic flow.

[0031] The manufacturing method of this invention solves the problems of machining accuracy and dynamic balance assurance for the drive housing as an irregularly shaped part. Before the first machining, the blank substrate is tempered to improve the substrate strength and eliminate internal stress, while laying the foundation for subsequent surface heat treatment to improve hardness. After the first machining, nitriding is used for surface heat treatment, and the substrate has been pre-tempered. This improves the surface hardness while minimizing the deformation caused by surface heat treatment, ensuring the positional accuracy between the geometric elements established by the first machining, and reducing the dynamic balance deviation of the finished product. During the hard cutting machining after surface heat treatment, one end is cut first, and then this end is used as the positioning reference for secondary clamping for finishing other geometric elements. The positioning principle of mutual reference is adopted to maximize the positional accuracy between the finishing geometric elements. After machining is completed, the components that rotate with it are installed on the drive housing, and dynamic balance is checked. The positioning clamping position during the check is consistent with the actual positioning position used, maximizing the dynamic balance of the entire component for final installation. Attached Figure Description

[0032] Figure 1 A preferred embodiment of the present invention is a dynamic balancing cut finished product isometric measurement Figure 1 ;

[0033] Figure 2 A preferred embodiment of the present invention is a dynamic balancing cut finished product isometric measurement Figure 2 ;

[0034] Figure 3 A preferred embodiment of the present invention is a dynamic balancing cut finished product isometric measurement Figure 3 ;

[0035] Figure 4 This is an isometric view of the unbalanced cut semi-finished product according to a preferred embodiment of the present invention;

[0036] Figure 5 This is a cross-sectional view of the unbalanced cut semi-finished product XX according to a preferred embodiment of the present invention;

[0037] Figure 6 This is a left view of the unbalanced cut semi-finished product according to a preferred embodiment of the present invention;

[0038] Figure 7 This is a right view of the unbalanced cut semi-finished product according to a preferred embodiment of the present invention;

[0039] Figure 8 This is a cross-sectional view of the unbalanced cut semi-finished product YY according to a preferred embodiment of the present invention;

[0040] Figure 9 This is a front view of the dynamically balanced cut finished product according to a preferred embodiment of the present invention;

[0041] Figure 10This is a right view of the dynamically balanced cut product according to a preferred embodiment of the present invention;

[0042] Figure 11 This is a left view of the dynamically balanced cut product according to a preferred embodiment of the present invention;

[0043] Figure 12 This is a top view of the dynamically balanced cut product according to a preferred embodiment of the present invention;

[0044] Figure 13 This is a rear view of the dynamically balanced cut product according to a preferred embodiment of the present invention;

[0045] Figure 14 This is a cross-sectional view of the dynamically balanced cut product ZZ according to a preferred embodiment of the present invention. Implementation

[0046] 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.

[0047] See Figures 1-14 The geometric elements set on the hydraulic-mechanical mixing drive housing include: 1. Main shaft bearing cavity; 2. Housing input end face; 3. Outer bearing support circle; 4. Bearing gear ring transition outer circle; 5. Gear ring transmission outer circle; 6. Bearing left end face; 7. Transition arc one; 8. Transition arc two; 9. Transition arc three; 10. Cylinder bearing outer circle; 11. Eccentric outer circle; 12. Cylinder bearing thrust surface; 13. Cylinder bearing cavity; 14. Cylinder bearing transition cavity; 15. Eccentric inner cavity; 16. Eccentric thrust surface; 17. Housing output end face; 18. Transition arc four; 19. Drive bearing retaining ring 2. 0. Drive bearing cavity 21. Housing outer conical surface 22. Bearing right end face 23. Transmission pin hole 24. Transition end face 25. Outer bearing thrust surface 26. Main bearing thrust surface 27. Main shaft through hole 28. Flushing inner cavity 29. Drive bearing thrust surface 30. Fastening screw hole 31. Left oblique cut surface 32. Left cut surface 33. Lower cut surface 34. Right cut surface 35. Right oblique cut surface 36. Oblique conical surface 37. Drive transition cavity 38. And the center line C formed by geometric elements, the right deflection rotation line E in the left view, the inclined axis T and the included angle K;

[0048] The center line C is parallel to the right-angled rotation line E in the left view. The center line C intersects the inclined axis T at an angle K to form a plane. This plane is perpendicular to the deviation of the right-angled rotation line E from the center line C in the direction of its deviation from the normal.

[0049] The outer periphery of the drive housing is provided with the following components in sequence from the housing input end face 2 to the housing output end face 18: outer bearing support circle 3, bearing gear ring transition outer circle 4, gear ring transmission outer circle 5, bearing outer circle 6, housing outer conical surface 22, cylinder bearing outer circle 11, and eccentric outer circle 12. The outer bearing support circle 3, bearing gear ring transition outer circle 4, gear ring transmission outer circle 5, bearing outer circle 6, housing outer conical surface 22, and cylinder bearing outer circle 11 are coaxial about the center line C. The rotation axis of the eccentric outer circle 12 is the right-biased rotation line E in the left view.

[0050] The inner cavity of the drive housing is provided with the following components in sequence from the output end face 18 of the housing to the input end face 2 of the housing: eccentric inner cavity 16, cylinder bearing transition cavity 15, cylinder bearing cavity 14, drive transition cavity 38, drive bearing retaining ring 20, drive bearing cavity 21, flushing inner cavity 29, main shaft through hole 28, and main shaft bearing cavity 1. The rotation axis of the eccentric inner cavity 16 is the right-biased rotation line E in the left view. The eccentric inner cavity 16 is coaxial with the eccentric outer circle 12 and the rotation axis is the right-biased rotation line E in the left view. The cylinder bearing transition cavity 15, cylinder bearing cavity 14, main shaft through hole 28, and main shaft bearing cavity 1 are coaxial and the rotation axis is the center line C. The drive transition cavity 38, drive bearing retaining ring 20, drive bearing cavity 21, and flushing inner cavity 29 are coaxial and the rotation axis is the inclined axis T.

[0051] Due to the offset of the drive bearing retaining ring 20, drive bearing cavity 21, flushing cavity 29, drive transition cavity 38, and transmission pin hole 24, the center of gravity of the drive housing before dynamic balancing cutting is not on the center line C. It is necessary to cut and remove the material on the periphery of the drive housing to achieve dynamic balance and reduce weight, thereby reducing rotational inertia. The material removed from the periphery of the drive housing after cutting forms a left oblique cutting surface 32, a left cutting surface 33, a lower cutting surface 34, a right cutting surface 35, and a right oblique cutting surface 36. In order to facilitate balance adjustment, the main body material of the cylinder bearing transition cavity 15 corresponding to the eccentric direction is further cut to form an oblique conical surface 37.

[0052] In this embodiment, the diameter of the outer bearing support circle 3 is smaller than the diameter of the bearing gear ring transition outer circle 4. An outer bearing thrust surface 26 is formed between the outer bearing support circle 3 and the bearing gear ring transition outer circle 4. The diameter of the bearing gear ring transition outer circle 4 is smaller than the diameter of the gear ring drive outer circle 5. A transition end face 25 is formed between the bearing gear ring transition outer circle 4 and the gear ring drive outer circle 5. The diameter of the gear ring drive outer circle 5 is smaller than the diameter of the bearing outer circle 6. A bearing right end face 23 is formed between the gear ring drive outer circle 5 and the bearing outer circle 6. A drive pin hole 24 and a fastening screw hole 31 are provided on the bearing right end face 23 side. The drive pin hole 24 and the fastening screw hole 31 are located between the gear ring drive outer circle 5 and the bearing outer circle 6. The rotation axes of the transmission pin hole 24 and the fastening screw hole 31 are perpendicular to the right end face 23 of the bearing, respectively. The half cone angle of the outer conical surface 22 of the housing is consistent with the included angle K. The large circle diameter of the outer conical surface 22 of the housing is smaller than the diameter of the outer circle 6 of the bearing. The small circle diameter of the outer conical surface 22 of the housing is smaller than the diameter of the outer circle 11 of the cylinder bearing. The left end face 7 of the bearing is connected to the large circle end of the outer conical surface 22 of the housing through transition arc 1 8. The small circle end of the outer conical surface 22 of the housing is connected to the outer circle 11 of the cylinder bearing through continuous intersecting transition arcs 2 9 and 3 10. The diameter of the outer circle 11 of the cylinder bearing is smaller than that of the eccentric outer circle 12. The outer circle 11 of the cylinder bearing and the eccentric outer circle 12 are connected through transition arc 4 19.

[0053] In this embodiment, the diameter of the cylinder bearing transition cavity 15 is larger than the diameter of the cylinder bearing cavity 14, the diameter of the eccentric inner cavity 16 is larger than the diameter of the cylinder bearing transition cavity 15, an eccentric thrust surface 17 is formed between the eccentric inner cavity 16 and the cylinder bearing transition cavity 15, a tool relief groove is provided at the intersection of the eccentric inner cavity 16 and the eccentric thrust surface 17, a cylinder bearing thrust surface 13 is formed between the drive transition cavity 38 and the cylinder bearing cavity 14, the diameter of the drive bearing cavity 21 is larger than the diameter of the drive transition cavity 38, and a drive bearing retaining ring 20 is provided between the drive bearing cavity 21 and the drive transition cavity 38, and the diameter of the flushing inner cavity 29 is smaller than that of the drive bearing cavity 28. The diameter of the flushing inner cavity 29 is 1. A drive bearing thrust surface 30 is formed between the flushing inner cavity 29 and the drive bearing cavity 21. The main shaft through hole 28 penetrates the drive housing. One end of the main shaft through hole 28 is connected to the flushing inner cavity 29 and the other end is connected to the main shaft bearing cavity 1. A main bearing thrust surface 27 is formed between the main shaft through hole 28 and the main shaft bearing cavity 1. The housing output end face 18, the eccentric thrust surface 17, the cylinder bearing thrust surface 13, the main bearing thrust surface 27, the housing input end face 2, the bearing left end face 7, the bearing right end face 23, the transition end face 25, and the outer bearing thrust surface 26 are perpendicular to the center line C. The drive bearing thrust surface 30 is perpendicular to the inclined axis T.

[0054] In this embodiment, when the drive housing is in driving condition, bearings are respectively provided on the cylinder bearing cavity 14, drive bearing cavity 21, main shaft bearing cavity 1, and outer bearing support circle 3. The inner ring of the bearing in the cylinder bearing cavity 14 is installed on the plunger cylinder body, the inner ring of the bearing in the main shaft bearing cavity 1 is installed on the main shaft, the main shaft and the plunger cylinder body are coaxially fixed, and the outer ring of the bearing in the outer bearing support circle 3 is installed on the housing. The bearings provided in the cylinder bearing cavity 14, main shaft bearing cavity 1, and outer bearing support circle 3 complete the positioning and load transmission of the drive housing. The drive housing can only rotate around the center line C. The main shaft passes through the main shaft through hole 28 and the main shaft bearing cavity 1, and the end face of the plunger cylinder body extends into the drive transition cavity 38.

[0055] In this embodiment, a transmission gear is provided on the outer circle 5 of the gear ring drive. The pin shaft provided in the transmission pin hole 24 is also provided on the transmission gear, thereby limiting the circumferential position of the transmission gear relative to the drive housing. The screw passes through the transmission gear and is screwed into the fastening screw hole 31, thereby fastening the transmission gear to the drive housing. The power source drives the drive housing to rotate through the transmission gear.

[0056] In this embodiment, an eccentric ring is provided inside the eccentric inner cavity 16. The eccentric inner cavity 16 drives and controls the flow distribution valve through the eccentric ring, and the eccentric thrust surface 17 restricts the axial position of the eccentric ring on one side.

[0057] In this embodiment, one side of the outer ring of the bearing installed in the cylinder bearing cavity 14 contacts and limits the cylinder bearing thrust surface 13. The cylinder bearing transition cavity 15 facilitates the installation of the bearing into the cylinder bearing cavity 14. One side of the outer ring of the bearing installed in the main shaft bearing cavity 1 contacts and limits the main bearing thrust surface 27 for bearing support. The inner ring of the bearing on the outer bearing support circle 3 contacts and limits the outer bearing thrust surface 26 for bearing support. One side of the outer ring of the bearing in the drive bearing cavity 21 contacts and limits the drive bearing thrust surface 30 for bearing support. The other side is limited by a retaining ring provided in the drive bearing retaining ring 20.

[0058] In this embodiment, a drive swashplate is provided on the inner ring of the bearing in the drive bearing cavity 21. The drive housing drives the plunger on the plunger cylinder through the drive swashplate. A radial oil outlet is provided on the main shaft in the main shaft through hole 28. Part of the oil entering the main shaft through hole 28 flows into the housing through the main shaft bearing cavity 1, and the other part flows back into the housing through the flushing inner cavity 29, drive bearing cavity 21, drive transition cavity 38, cylinder bearing cavity 14, cylinder bearing transition cavity 15, and eccentric inner cavity 16, thereby lubricating and cooling the bearing.

[0059] See Figures 1-14 The manufacturing method of the organic-hydraulic mixing drive housing includes the following specific steps:

[0060] Step 1: Perform quenching and tempering heat treatment on the drive housing blank;

[0061] Step 2: Perform the first machining on the geometric elements designed for the drive housing, with some geometric elements having machining allowances;

[0062] Step 3: Perform surface heat treatment on the drive housing after the first machining process;

[0063] Step 4: Perform finishing on the drive housing after surface heat treatment;

[0064] Step 5: Perform dynamic balancing on the finished drive housing.

[0065] In this embodiment, the blank material in step one is 38CrMoAl or 31CrMoV9, and the quenched and tempered hardness is greater than HRC20.

[0066] In this embodiment, the machining of the rotating body 1 in step two is completed in one clamping using a turning-boring-milling composite machining center to ensure the positional accuracy between the parts.

[0067] In step two, the blank holding the input end face 2 of the housing is machined for the first time. First, all the geometric contours of the inner cavity are machined, then the outer contour is machined, and finally it is cut off from the input end face 2 of the housing.

[0068] The geometric elements with machining allowances in the first machining process mentioned in step two include: spindle bearing cavity 1, outer bearing support circle 3, bearing gear ring transition outer circle 4, gear ring drive outer circle 5, cylinder bearing cavity 14, eccentric inner cavity 16, drive bearing cavity 21, cylinder bearing thrust surface 13, eccentric thrust surface 17, bearing right end face 23, outer bearing thrust surface 26, main bearing thrust surface 27, and drive bearing thrust surface 30.

[0069] In this embodiment, the surface heat treatment in step three is nitriding, the nitriding layer depth is greater than 0.3 mm, and the nitriding hardness is greater than HV780.

[0070] In this embodiment, the finishing process in step four involves first using a hard-cutting machine tool to clamp the outer circle 11 of the cylinder bearing and using the left end face 7 of the bearing as the axial positioning end face. After positioning and clamping, the spindle bearing cavity 1, the main bearing thrust surface 27, the outer bearing support circle 3, the outer bearing thrust surface 26, the gear ring drive outer circle 5, the right end face 23 of the bearing, and the bearing gear ring transition outer circle 4 are hard-cut. After the finishing process, the bearing gear ring transition outer circle 4 is clamped using a hard-cutting machine tool and using the right end face 23 of the bearing as the axial positioning end face. Then, the circumferential position of the drive housing is restricted by the transmission pin hole 24. After positioning and clamping, the eccentric inner cavity 16, the eccentric thrust surface 17, the cylinder bearing cavity 14, the cylinder bearing thrust surface 13, the drive bearing cavity 21, and the drive bearing thrust surface 30 are hard-cut.

[0071] In this embodiment, during the dynamic balancing calibration in step five, components that rotate with the drive housing are installed on the drive housing for dynamic balancing calibration.

[0072] 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 hydraulic-mechanical mixing drive housing, comprising a main shaft bearing cavity, a housing input end face, an outer bearing support circle, a bearing gear ring transition outer circle, a gear ring transmission outer circle, a load-bearing outer circle, a load-bearing left end face, transition arc one, transition arc two, transition arc three, a cylinder bearing thrust surface, an eccentric thrust surface, an outer bearing thrust surface, a main bearing thrust surface, a drive bearing thrust surface, a cylinder load-bearing outer circle, an eccentric outer circle, a cylinder bearing cavity, a cylinder bearing transition cavity, an eccentric inner cavity, a housing output end face, a drive bearing retaining ring, a drive bearing cavity, a housing outer conical surface, a load-bearing right end face, a transmission pin hole, a transition end face, a main shaft through hole, a flushing inner cavity, a fastening screw hole, a left oblique cutting surface, a left cutting surface, a lower cutting surface, a right cutting surface, a right oblique cutting surface, an oblique conical surface, a drive transition cavity, and a center line C, a right-biased rotation line E in the left view, an inclined axis T, and an included angle K, characterized in that, The center line C is parallel to the right-angled rotation line E in the left view. The center line C intersects the inclined axis T at an angle K to form a plane. This plane is perpendicular to the deviation of the right-angled rotation line E from the center line C in the direction of its deviation from the normal. The outer bearing support circle, bearing gear ring transition outer circle, gear ring drive outer circle, load-bearing outer circle, housing outer conical surface, cylinder load-bearing outer circle, and eccentric outer circle are sequentially set on the outer surface of the drive housing from the housing input end face to the housing output end. The outer bearing support circle, bearing gear ring transition outer circle, gear ring drive outer circle, load-bearing outer circle, housing outer conical surface, and cylinder load-bearing outer circle are coaxial about the center line C. The rotation axis of the eccentric outer circle is the right-biased rotation line E in the left view. An eccentric inner cavity, a cylinder bearing transition cavity, a cylinder bearing cavity, a drive transition cavity, a drive bearing retaining ring, a drive bearing cavity, a flushing inner cavity, a main shaft through hole, and a main shaft bearing cavity are sequentially arranged in the drive housing inner cavity from the housing output end face to the housing input end face. The eccentric inner cavity is coaxial with the eccentric outer circle and the axis of rotation is the right-biased rotation line E in the left view. The cylinder bearing transition cavity, the cylinder bearing cavity, the main shaft through hole, and the main shaft bearing cavity are coaxial and the axis of rotation is the center line C. The drive transition cavity, the drive bearing retaining ring, the drive bearing cavity, and the flushing inner cavity are coaxial and the axis of rotation is the inclined axis T. The left oblique cutting surface, left cutting surface, lower cutting surface, right cutting surface, and right oblique cutting surface are located on the periphery of the drive housing and are formed by cutting away material. The oblique conical cutting surface is formed on the main body material in the corresponding eccentric direction of the cylinder bearing transition cavity.

2. The machine-hydraulic mixing drive housing according to claim 1, characterized in that, During driving operation, the drive housing is equipped with bearings in the cylinder bearing cavity, drive bearing cavity, spindle bearing cavity, and outer bearing support circle. The inner ring of the bearing in the cylinder bearing cavity is mounted on the piston cylinder body, and the inner ring of the bearing in the spindle bearing cavity is mounted on the spindle. The spindle and the piston cylinder body are coaxially fixed. The outer ring of the bearing in the outer bearing support circle is mounted on the housing. The bearings in the cylinder bearing cavity, spindle bearing cavity, and outer bearing support circle complete the positioning and load transmission of the drive housing. The drive housing can only rotate around the center line C. The spindle passes through the spindle through hole and the spindle bearing cavity, and the end face of the piston cylinder body extends into the drive transition cavity. A transmission gear is provided on the outer circle of the gear ring drive. A pin is provided in the transmission pin hole and is also provided on the transmission gear to limit the circumferential position of the transmission gear relative to the drive housing. A screw passes through the transmission gear and is screwed into the fastening screw hole to fasten the transmission gear to the drive housing. The power source drives the drive housing to rotate through the transmission gear. An eccentric ring is provided inside the eccentric cavity. The eccentric cavity drives and controls the flow distribution valve through the eccentric ring. The eccentric thrust surface restricts the axial position of the eccentric ring on one side. One side of the outer ring of the bearing installed in the cylinder bearing cavity contacts and limits the cylinder bearing thrust surface. The cylinder bearing transition cavity facilitates the installation of the bearing into the cylinder bearing cavity. One side of the outer ring of the bearing installed in the main shaft bearing cavity contacts and limits the main bearing thrust surface. The inner ring of the bearing on the outer bearing support circle contacts and limits the outer bearing thrust surface. One side of the outer ring of the bearing in the drive bearing cavity contacts and limits the drive bearing thrust surface, while the other side is limited by a retaining ring set in the drive bearing retaining ring. A drive swashplate is installed on the inner ring of the bearing inside the drive bearing cavity. The drive housing drives the plunger on the plunger cylinder through the drive swashplate. A radial oil outlet is provided on the main shaft in the main shaft through hole. Part of the oil entering the main shaft through hole flows into the housing through the main shaft bearing cavity, and the other part flows back to the housing through the flushing inner cavity, drive bearing cavity, drive transition cavity, cylinder bearing cavity, cylinder bearing transition cavity, and eccentric inner cavity.

3. The machine-fluid mixing drive housing according to claim 1 or 2, characterized in that, The outer bearing support circle is smaller than the bearing gear ring transition outer circle. The outer bearing support circle and the bearing gear ring transition outer circle form the outer bearing thrust surface. The bearing gear ring transition outer circle is smaller than the gear ring drive outer circle. The bearing gear ring transition outer circle and the gear ring drive outer circle form a transition end face. The gear ring drive outer circle is smaller than the load-bearing outer circle. The gear ring drive outer circle and the load-bearing outer circle form the load-bearing right end face. The cylinder load-bearing outer circle is smaller than the eccentric outer circle. The cylinder load-bearing outer circle and the eccentric outer circle are connected by a transition arc.

4. The machine-fluid mixing drive housing according to claim 1 or 2, characterized in that, The cylinder bearing transition cavity is larger than the cylinder bearing cavity, the eccentric inner cavity is larger than the cylinder bearing transition cavity, and an eccentric thrust surface is formed between the eccentric inner cavity and the cylinder bearing transition cavity. A tool relief groove is provided at the intersection of the eccentric inner cavity and the eccentric thrust surface. A cylinder bearing thrust surface is formed between the drive transition cavity and the cylinder bearing cavity. The drive bearing cavity is larger than the drive transition cavity, and a drive bearing retaining ring is provided between the drive bearing cavity and the drive transition cavity. The flushing inner cavity is smaller than the drive bearing cavity, and a drive bearing thrust surface is formed between the flushing inner cavity and the drive bearing cavity.

5. The machine-fluid mixing drive housing according to claim 1 or 2, characterized in that, A drive pin hole and a fastening screw hole are provided on the right end face of the bearing. The drive pin hole and the fastening screw hole are located between the outer circle of the gear ring drive and the outer circle of the bearing, and the rotation axes of the drive pin hole and the fastening screw hole are perpendicular to the right end face of the bearing.

6. The machine-fluid mixing drive housing according to claim 1 or 2, characterized in that, The semi-cone angle of the outer conical surface of the shell is the same as the included angle K. The diameter of the large circle end of the outer conical surface of the shell is smaller than the diameter of the outer circle of the bearing. The diameter of the small circle end of the outer conical surface of the shell is smaller than the diameter of the outer circle of the bearing of the cylinder. The left end face of the bearing is connected to the large circle end of the outer conical surface of the shell through transition arc one. The small circle end of the outer conical surface of the shell is connected to the outer circle of the bearing of the cylinder through continuous intersecting transition arc two and transition arc three.

7. The machine-fluid mixing drive housing according to claim 1 or 2, characterized in that, The main shaft through hole penetrates the drive housing. One end of the main shaft through hole is connected to the flushing inner cavity and the other end is connected to the main shaft bearing cavity. The main shaft through hole and the main shaft bearing cavity form the main bearing thrust surface. The housing output end face, housing input end face, bearing left end face, bearing right end face, and transition end face are perpendicular to the center line C.

8. A method for manufacturing a mechanical-hydraulic mixing drive housing, used in the mechanical-hydraulic mixing drive housing according to claim 1, characterized in that, The specific steps are as follows: Step 1: Perform quenching and tempering heat treatment on the drive housing blank; Step 2: Perform the first machining on the geometric elements designed for the drive housing, with some geometric elements having machining allowances; Step 3: Perform surface heat treatment on the drive housing after the first machining process; Step 4: Perform finishing on the drive housing after surface heat treatment; Step 5: Perform dynamic balancing on the finished drive housing.

9. The method for manufacturing the machine-fluid mixing drive housing according to claim 8, characterized in that, The blank material in step one is alloy steel with a tempering hardness greater than HRC20; The surface heat treatment in step three is nitriding, with a nitriding layer depth greater than 0.3 mm and a nitriding hardness greater than HV700.

10. The method for manufacturing the machine-fluid mixing drive housing according to claim 8, characterized in that, In step two, the machining of the drive housing is completed in one setup using a turning-boring-milling composite machining center. In step two, the blank holding the input end face of the housing is subjected to the first machining. First, all the geometric contours of the inner cavity are machined, then the outer contour is machined, and finally it is cut off from the input end face of the housing. The geometric elements with machining allowance in the first machining step of step two include: spindle bearing cavity, outer bearing support circle, bearing gear ring transition outer circle, gear ring drive outer circle, cylinder bearing cavity, eccentric inner cavity, drive bearing cavity, cylinder bearing thrust surface, eccentric thrust surface, outer bearing thrust surface, main bearing thrust surface, drive bearing thrust surface, and bearing right end face.

11. The method for manufacturing the machine-fluid mixing drive housing according to claim 8, characterized in that, In step four, the finishing process involves first using a hard-cutting machine tool to clamp the outer circle of the cylinder bearing and using the left end face of the bearing as the axial positioning end face. After positioning and clamping, the spindle bearing cavity, main bearing thrust surface, outer bearing support circle, gear ring drive outer circle, bearing right end face, and bearing gear ring transition outer circle are hard-cut. In the second clamping, the bearing gear ring transition outer circle is clamped using a hard-cutting machine tool and the right end face of the bearing is used as the axial positioning end face. Then, the circumferential position of the drive housing is restricted by the transmission pin hole. After positioning and clamping, the eccentric inner cavity, eccentric thrust surface, cylinder bearing cavity, and drive bearing cavity are hard-cut.

12. The method for manufacturing the machine-fluid mixing drive housing according to claim 8, characterized in that, During the dynamic balancing calibration in step five, components that rotate with the drive housing are installed on the drive housing, and the spindle bearing cavity and cylinder bearing cavity are used as positioning references for dynamic balancing calibration.

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