A continuously variable gear pump

Abstract

This invention relates to the field of cable technology, and more particularly to a continuously variable gear pump, comprising: a housing and a power component disposed inside the housing. A water inlet is provided on the surface of the housing, penetrating the side of the housing. The power component includes a driven shaft and a drive shaft with one end extending outward from the outside of the housing. Gears are integrally formed on the outer sides of the drive shaft and the driven shaft, meshing with each other. The water inlet faces the meshing point of the gears. A first one-way bearing is fixed to the end of the drive shaft. A lead screw is fixed to the inner side of the first one-way bearing. A moving block is threaded to the outer side of the lead screw. A sealing component is provided between the moving block and the gear. A second one-way bearing, fixed to the housing, is connected to the outer side of the other end of the lead screw. A torsion spring is embedded at the end of the lead screw. The first and second one-way bearings rotate in opposite directions. This invention relies on the self-locking of the trapezoidal lead screw to ensure stable operation after displacement adjustment, and utilizes the combination of the one-way bearing and the torsion spring to achieve precise and efficient reset of the adjusting components.

Description

Technical Field

[0001] This invention relates to the field of cable technology, and more particularly to a continuously variable gear pump. Background Technology

[0002] As the core power component of hydraulic transmission systems, gear pumps have been widely used in many industrial fields such as engineering machinery, industrial automation, mining machinery, and agricultural machinery due to their outstanding advantages such as simple structure, reliable operation, excellent self-priming performance, and wide speed adaptability.

[0003] Existing gear pumps are mainly divided into two categories: fixed displacement gear pumps and variable displacement gear pumps. The displacement of a fixed displacement gear pump is determined by core structural parameters such as gear module, number of teeth, and tooth width, and cannot be adjusted once manufactured. In actual operation, to meet different flow requirements, auxiliary components such as throttle valves and relief valves are often needed for flow regulation. This method not only causes a large amount of energy to be wasted as heat, but also leads to severe overheating of the hydraulic system, accelerating the aging and deterioration of seals, hydraulic oil, and other components, significantly reducing the operational stability and overall service life of the hydraulic system.

[0004] To address the inherent defects of fixed-displacement gear pumps, various variable-displacement gear pumps have emerged. However, existing variable-displacement gear pumps still have many technical limitations. For example, Chinese patent CN115898860A discloses a variable-displacement gear pump whose gear pair consists of a set of fixed-displacement gear pairs and several sets of variable-displacement gear pairs. Displacement adjustment is achieved by changing the number of meshing gear pairs. This solution can only achieve step-by-step displacement switching and cannot meet the continuous and precise flow control requirements of high-end hydraulic systems. Another Chinese patent CN115898860A discloses adjusting the displacement by manually operating or using a computer-controlled combined control lever outside the gear pump chamber, thereby changing the meshing length of the gears inside the pump. This type of external adjustment mechanism not only increases the structural complexity of the pump body but also easily causes hydraulic oil leakage at the adjustment interface. In addition, the long-term reciprocating operation of the external lever can easily lead to seal failure, further exacerbating the risk of leakage. Summary of the Invention

[0005] To address the shortcomings of existing technologies, this invention provides the following technical solution: A continuously variable gear pump includes: a housing and a power component disposed inside the housing.

[0006] Specifically, the surface of the housing has a water inlet that penetrates the side of the housing. The power component includes a driven shaft and a drive shaft with one end extending out of the outside of the housing. The drive shaft and the driven shaft have interlocking gears integrally formed on their outer sides. The water inlet faces the meshing point of the gears. A one-way bearing is fixed to the end of the drive shaft. A lead screw is fixed to the inner side of the one-way bearing. A moving block is threaded to the outer side of the lead screw. A sealing component is provided between the moving block and the gear. A second one-way bearing, which is fixed to the housing, is connected to the outer side of the other end of the lead screw. A torsion spring is embedded at the end of the lead screw. The rotation directions of the first and second one-way bearings are opposite.

[0007] As an improvement to the above technical solution, a front cover is provided on the side of the housing near the end of the drive shaft that protrudes outward. A front sliding bearing I and a front sliding bearing II are provided inside the front cover. The ends of the drive shaft and the driven shaft are inserted into the interior of the front sliding bearing I and the front sliding bearing II. A front thrust ball bearing and a support I are provided on the outside of the front sliding bearing I. The front thrust ball bearing is located between the support I and the front cover.

[0008] As an improvement to the above technical solution, a rear end cover is provided inside the housing, and a rear sliding bearing one and a rear sliding bearing two are provided inside the rear end cover. The tail of the drive shaft is inserted into the interior of the rear sliding bearing one, and the tail of the driven shaft is inserted into the interior of the rear sliding bearing two. A support two is provided on the outer side of the rear sliding bearing two.

[0009] As an improvement to the above technical solution, the housing has openings at both ends and an elliptical cavity inside. The two opening sides of the housing are detachably provided with caps, and the tail of the rear cover is provided with a limit block. The tail of the driven shaft is detachably fixed to the limit block.

[0010] As an improvement to the above technical solution, the sealing component includes a toothed groove filling block one and a toothed groove filling block two. A circular groove is opened on one side of the support one and the support two. The toothed groove filling block one and the toothed groove filling block two are disposed in the corresponding circular grooves. The toothed groove filling block one and the toothed groove filling block two respectively fill the outside of the gears of the drive shaft and the driven shaft and form a seal to separate and form a sealed cavity. The water inlet is connected to the sealed cavity.

[0011] As an improvement to the above technical solution, a fixing ring two is provided between the front thrust ball bearing and the toothed groove filling block one. The fixing ring two has a number of pins fixed on the side near the toothed groove filling block one, which are the same as the number of pins in the toothed groove filling block one. The pins are inserted into the interior of the toothed groove filling block one. A rear thrust ball bearing is provided on the outer side of the rear sliding bearing one. The rear thrust ball bearing fits against the rear end cover. A fixing ring one is provided between the rear thrust ball bearing and the toothed groove filling block two. The fixing ring one has a number of pins fixed on the side near the toothed groove filling block two, which are the same as the number of pins in the toothed groove filling block two. The pins are inserted into the interior of the toothed groove filling block two.

[0012] As an improvement to the above technical solution, a bearing support is provided inside the housing, the lead screw includes a rod body, a rear groove is provided at the end of the rod body away from the drive shaft, the torsion spring is disposed inside the rear groove, the one-way bearing is disposed inside the bearing support, the tail of the drive shaft passes through the one-way bearing and is inserted into the bearing support, one end of the torsion spring is detachably fixed to the rear groove, and the other end of the torsion spring is detachably fixed to the inner wall of the bearing support.

[0013] As an improvement to the above technical solution, the inner wall of the one-way bearing is provided with a serrated groove, and a lead screw bushing is fixed on the outer side of the end of the drive shaft located inside the one-way bearing. A keyway is provided on the outer side of the lead screw bushing, and a T-key is provided between the keyway and the serrated groove. The end of the T-key inserted into the keyway and the inner side of the serrated groove is made of magnetic material, and the groove opening of the serrated groove faces the moving block.

[0014] As an improvement to the above technical solution, the one-way bearing includes an outer ring, a roller cage disposed inside the outer ring, and an inner ring disposed inside the roller cage, wherein the serrated groove is formed on the inner wall of the inner ring.

[0015] As an improvement to the above technical solution, an annular groove is provided on the side of the moving block near the one-way bearing, and the other end of the T-key is inserted into the interior of the annular groove.

[0016] The beneficial effects of this invention are: The axial sliding design of the sealing component enables continuous stepless adjustment of the displacement; the self-locking characteristic of the trapezoidal screw ensures stable and reliable operation after displacement adjustment; the combination of one-way bearing and torsion spring completes the precise and efficient reset of the adjustment components; and all functional components are integrated inside the pump cavity to form a closed protective structure, effectively ensuring the overall sealing performance of the pump body. Attached Figure Description

[0017] Figure 1 This is a three-dimensional structural diagram of the present invention; Figure 2 This is an exploded structural diagram from a first-view perspective of the present invention; Figure 3 for Figure 2 Enlarged structural diagram at point A in the middle; Figure 4 for Figure 2 Enlarged structural diagram at point B; Figure 5 for Figure 2 Enlarged structural diagram at point C; Figure 6 This is a three-dimensional structural diagram of the present invention from a second perspective; Figure 7 for Figure 6 Enlarged structural diagram at point D; Figure 8 This is a structural diagram of the lead screw, the inner ring of the one-way bearing, the lead screw bushing, and the moving block of the present invention. Figure 9 This is a side view of the present invention; Figure 10 for Figure 9 An isometric side sectional view at point aa; Figure 11 This is a schematic diagram of the lead screw bushing and outer ring of the present invention under ω rotation direction; Figure 12 This is a schematic diagram of the lead screw bushing and outer ring of the present invention in the -ω direction of rotation. Figure 13 This is a schematic diagram of the first state between the T-key and the outer ring of the present invention; Figure 14 This is a schematic diagram of the second state between the T-key and the outer ring of the present invention.

[0018] Reference numerals: 10, casing; 11, cover; 20. Power component; 21. Drive shaft; 211. Gear; 212. Front sliding bearing 1; 213. Rear sliding bearing 1; 214. Rear thrust ball bearing; 215. Retaining ring 1; 22. Driven shaft; 221. Front sliding bearing II; 222. Front thrust ball bearing; 223. Retaining ring II; 224. Rear sliding bearing II; 23. Lead screw; 2301. Screw body; 2302. Back groove; 231. Moving block; 232. T-key; 233. Lead screw bushing; 2331. Keyway; 234. One-way bearing; 2341. Inner ring; 2342. Roller cage; 2343. Outer ring; 2344. Serrated groove; 235. Bearing support; 236. Torsion spring; 24. Front cover; 25. Rear cover; 251. Limiting block; 252. One-way bearing II; 26. Support I; 261. Tooth groove filling block I; 27. Support II; 271. Tooth groove filling block II. Detailed Implementation

[0019] The following specific examples illustrate the implementation of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through other different specific embodiments, and various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention.

[0020] Existing variable gear pumps still have many technical limitations. For example, Chinese patent CN115898860A discloses a variable gear pump whose gear pair consists of a set of fixed gear pairs and several sets of variable gear pairs. The displacement is adjusted by changing the number of meshing gear pairs. This solution can only achieve step-like displacement switching and cannot meet the continuous and precise flow control requirements of high-end hydraulic systems. Chinese patent CN115898860A also discloses adjusting the displacement by manually or computer-controlled joint control levers outside the pump chamber, changing the meshing length of the gears inside the pump through external operation. Such external adjustment mechanisms not only increase the structural complexity of the pump body, but also easily cause hydraulic oil leakage at the adjustment interface. At the same time, the long-term reciprocating operation of the external levers can easily lead to seal failure, further aggravating the risk of leakage.

[0021] To resolve the above issues, please refer to Figures 1 to 14 A continuously variable gear pump is provided, comprising: a housing 10 and a power component 20 disposed inside the housing 10.

[0022] Specifically, the surface of the housing 10 is provided with a water inlet that penetrates the side of the housing 10. The power component 20 includes a driven shaft 22 and a drive shaft 21 that extends out of the outer side of the housing 10. The drive shaft 21 and the driven shaft 22 are integrally formed with meshing gears 211. The water inlet faces the meshing part of the gears 211. A one-way bearing 234 is fixed to the end of the drive shaft 21. A lead screw 23 is fixed to the inner side of the one-way bearing 234. A moving block 231 is threaded to the outer side of the lead screw 23. A sealing component is provided between the moving block 231 and the gear 211. A two-way bearing 252 fixed to the housing 10 is connected to the outer side of the other end of the lead screw 23. A torsion spring 236 is embedded at the end of the lead screw 23. The rotation directions of the one-way bearing 234 and the one-way bearing 252 are opposite.

[0023] Since the rotation directions of one-way bearing 234 and one-way bearing 252 are inconsistent, two different control methods can be achieved by controlling the rotation direction of the drive shaft 21. When one-way bearing 234 is locked and one-way bearing 252 is in a free state, the lead screw 23 can rotate with the drive shaft 21. Under the restriction of the moving block 231, the lead screw 23 itself will not move, but will push the moving block 231 on its outer side to move. The moving block 231 pushes the sealing part, thereby reducing the meshing space between the two gears 211, thus achieving the method of controlling the displacement. When one-way bearing 234 is in a free state and one-way bearing 252 is locked, the torsion spring 236 will play a role, and its restoring deformation force will push the structure to slowly reset.

[0024] In one embodiment, the support and stabilizing structure inside the housing 10 is designed as follows: A front cover 24 is provided inside the housing 10 near the end of the drive shaft 21 that protrudes outward. A front sliding bearing 212 and a front sliding bearing 221 are provided inside the front cover 24. The ends of the drive shaft 21 and the driven shaft 22 are inserted into the front sliding bearing 212 and the front sliding bearing 221. A front thrust ball bearing 222 and a support 26 are provided on the outside of the front sliding bearing 212. The front thrust ball bearing 222 is located between the support 26 and the front cover 24.

[0025] The front cover 24 and the support 26 fix and support the front ends of the drive shaft 21 and the driven shaft 22. The front sliding bearing 212 and the front sliding bearing 221 ensure the stability of the rotation of the drive shaft 21 and the driven shaft 22. In order to ensure the stability of the structure, the following restrictions are given on this basis: The housing 10 has a rear end cover 25 inside, and a rear sliding bearing 213 and a rear sliding bearing 224 are installed inside the rear end cover 25. The tail of the drive shaft 21 is inserted into the rear sliding bearing 213, and the tail of the driven shaft 22 is inserted into the rear sliding bearing 224. A support 27 is provided on the outside of the rear sliding bearing 224.

[0026] Furthermore, the rear end cover 25, along with the corresponding rear sliding bearing 224 and support 27, provides fixation and support at the tail of the shaft. This, in conjunction with the front end cover 24 and the corresponding support 26, forms support and positioning at both ends, ensuring the stability of the structure during operation.

[0027] In one embodiment, see Figure 2 and Figure 4The housing 10 has openings at both ends and an elliptical cavity inside. The two opening sides of the housing 10 are detachably provided with a cover 11. The tail of the rear cover 25 is provided with a limit block 251. The tail of the driven shaft 22 is detachably fixed to the limit block 251.

[0028] The structure of the housing 10 is further improved by sealing it with caps 11 at both ends. The inner cavity is elliptical, which can provide rotation for the drive shaft 21 and driven shaft 22 while restricting the rotation of the corresponding support 26 and support 27, thereby enhancing the compactness of the internal structure.

[0029] Based on the aforementioned technical solution, the structural components of the sealing element are further improved, and the specific design is as follows: The sealing component includes a toothed groove filling block 261 and a toothed groove filling block 271. A circular groove is provided on one side of the support 26 and the support 27. The toothed groove filling block 261 and the toothed groove filling block 271 are disposed in the corresponding circular grooves. The toothed groove filling block 261 and the toothed groove filling block 271 respectively fill the outside of the gear 211 of the drive shaft 21 and the driven shaft 22 and form a seal to separate and form a sealed cavity. The water inlet is connected to the sealed cavity.

[0030] The number of tooth groove filling blocks 261 and 271 is consistent with the number of teeth of gear 211. Their cross-sectional shape is perfectly matched with the tooth groove, and their outer surface is flush with the tooth surface of the drive wheel. This ensures the sealing of the hydraulic oil chamber when gear 211 is meshing and avoids hydraulic oil leakage that would reduce volumetric efficiency.

[0031] To ensure the stability of the toothed filling block 261 and the toothed filling block 271, the following design is given in this embodiment: A retaining ring 223 is provided between the front thrust ball bearing 222 and the toothed filling block 261. The retaining ring 223 is fixed with a number of pins equal to the number of toothed filling blocks 261 on the side near the toothed filling block 261. The pins are inserted into the interior of the toothed filling block 261. A rear thrust ball bearing 214 is provided on the outside of the rear sliding bearing 213. The rear thrust ball bearing 214 is in contact with the rear end cover 25. A retaining ring 215 is provided between the rear thrust ball bearing 214 and the toothed filling block 271. The retaining ring 215 is fixed with a number of pins equal to the number of toothed filling blocks 271 on the side near the toothed filling block 271. The pins are inserted into the interior of the toothed filling block 271.

[0032] By cooperating with the second fixed ring 223 and the first fixed ring 215, the positions of each toothed filling block 261 and the second toothed filling block 271 are fixed. The front thrust ball bearing 222 and the rear thrust ball bearing 214 are provided to bear the axial load of fluid pressure applied to the toothed filling block 261 and the second toothed filling block 271, preventing the first fixed ring 215 and the second fixed ring 223 of the toothed filling block 261 and the second toothed filling block 271 from rotating and wearing due to the pressure, thus extending the service life of the components.

[0033] While the aforementioned technical solution explains the rebound function of the torsion spring 236, its specific structural details are not fully elaborated. Based on this, this embodiment presents the following design: The housing 10 has a bearing support 235 inside. The lead screw 23 includes a rod body 2301. The end of the rod body 2301 away from the drive shaft 21 has a rear groove 2302. The torsion spring 236 is disposed inside the rear groove 2302. The one-way bearing 234 is disposed inside the bearing support 235. The tail of the drive shaft 21 passes through the one-way bearing 234 and is inserted into the bearing support 235. One end of the torsion spring 236 is detachably fixed to the rear groove 2302, and the other end of the torsion spring 236 is detachably fixed to the inner wall of the bearing support 235.

[0034] By providing a rear groove 2302 at the tail of the lead screw 23, space is provided at its tail for installing the torsion spring 236. Although not shown in detail in the accompanying drawings, it should be understood that in this embodiment, the corresponding position of the bearing support 235 should also be provided in the groove of the rear groove 2302 corresponding to the groove used to engage the torsion spring 236. By cooperating with the rear groove 2302, the two ends of the torsion spring 236 can be fixed. Only when relative deflection occurs can the torsion spring 236 be twisted.

[0035] The aforementioned technical solution lacks further structural constraints, which may lead to unexpected reset states. To avoid this problem, the following design is proposed: The inner wall of the one-way bearing 234 is provided with a serrated groove 2344. The drive shaft 21 is located inside the one-way bearing 234 and the outer side of the end is fixed with a lead screw sleeve 233. The outer side of the lead screw sleeve 233 is provided with a keyway 2331. A T-key 232 is provided between the keyway 2331 and the serrated groove 2344. The end of the T-key 232 inserted into the inner side of the keyway 2331 and the serrated groove 2344 is made of magnetic material. The groove opening of the serrated groove 2344 faces the moving block 231.

[0036] The magnetism of the T-key 232 forms a reliable circumferential limit, thereby preventing the lead screw bushing 233 from unexpectedly resetting under the elastic restoring force of the torsion spring 236, and ensuring the stability of the adjusted state.

[0037] In this embodiment, the design of the one-way bearing 234 adopts a conventional one-way bearing, as shown below: One-way bearing 234 includes an outer ring 2343, a roller cage 2342 disposed inside the outer ring 2343, and an inner ring 2341 disposed inside the roller cage 2342.

[0038] In contrast, in this embodiment, the serrated groove 2344 is formed on the inner wall of the inner ring 2341. Based on this, in order to further stabilize the structure of the T-key 232, the following design is given: The movable block 231 has an annular groove on the side near the one-way bearing 234, and the other end of the T-key 232 is inserted into the annular groove.

[0039] The end of the T-key 232 is restricted by an annular groove. The end of the T-key 232 is an arc-shaped piece that engages inside the annular groove, thereby allowing it to turn along the inside of the annular groove. To make the technical solution provided in this embodiment easier for those skilled in the art to understand, the following explanation is given: Before starting the continuously variable gear pump, the initial settings for displacement adjustment must be completed to ensure that the pump enters the working state with the target displacement. The specific process is as follows: When displacement adjustment is required, the external power source drives the drive shaft 21 along... Figure 11 As shown, the screw rotates in the ω direction. At this time, the one-way bearing 252 in the adjustment drive assembly switches to the locked state, and the rotation of the lead screw 23 in the non-adjustment direction is restricted by the structural self-locking, providing a stable constraint for power transmission. The rotational power of the drive shaft 21 is transmitted to the lead screw 23 through the transmission link, causing the lead screw 23 to rotate synchronously in the ω direction; since the lead screw bushing 233 and the lead screw 23 are fixed together by an interference fit, the rotation of the lead screw 23 synchronously drives the rotation of the lead screw bushing 233.

[0040] During the rotation of the lead screw bushing 233, its keyway 2331 and the end of the T-key 232 form a reliable linkage through magnetic attraction, causing the T-key 232 to rotate synchronously with the lead screw bushing 233. Simultaneously, the other end of the T-key 232 magnetically attracts the serrated groove 2344 of the inner ring 2341 of the one-way bearing 234, thereby driving the inner ring 2341 of the one-way bearing 234 to rotate synchronously with the T-key 232. Because the one-way bearing 234 has a reverse locking characteristic, when the inner ring 2341 of the one-way bearing 234 rotates to a specific angle with the T-key 232, its locking structure is triggered and restricts its reverse rotation.

[0041] Under this constraint, the axial position of the lead screw 23 remains stable, and the moving block 231, which is threadedly engaged with the lead screw 23, cannot move axially, thus its axial position is fixed. Since the rear end cover 25 is positioned by the moving block 231, the fixed state of the moving block 231 synchronously ensures the axial position of the rear end cover 25 is stable. The limiting block 251 is fixed to the shaft end of the driven shaft 22 by bolts and is located on one side of the rear end cover 25. The fixed position of the rear end cover 25 drives the limiting block 251 to remain stable synchronously. Thus, through the axial constraint of the limiting block 251 on the driven shaft 22, the driven shaft 22 is pushed to move axially to a position that meshes with the drive shaft 21, thus completing the initial setting of the displacement adjustment and laying the foundation for the subsequent oil suction and discharge operation of the pump body.

[0042] At the same time, the torsion spring 236, which is sleeved in the end hole of the lead screw 23, gradually deforms as the lead screw 23 rotates, completing the elastic energy storage, reserving elastic restoring force for the subsequent adjustment component to reset, and ensuring that the displacement can be quickly reset when readjusted.

[0043] like Figure 12 As shown, when the drive shaft 21 rotates in the -ω direction, the gear pump enters the normal oil suction and discharge working state. Its core ensures that the effective meshing width of the driving and driven gears is consistent through the self-tightening effect of hydraulic oil pressure and the precise matching of axial dimensions, thereby achieving stable displacement. The specific process is as follows: When the hydraulic oil fills the pump chamber and forms a stable pressure, the pressure acts on the end faces of each component, forming an axial clamping force: the hydraulic oil pressure pushes the toothed filling block 271 and the fixing ring 215 to move axially toward the rear end cover 25, so that the three are tightly pressed together with the rear thrust ball bearing 214; the other side of the rear thrust ball bearing 214 is tightly pressed against the rear end cover 25, while the support 26 is pressed against the front end cover 24, forming axial positioning and sealing on the drive wheel side.

[0044] Similarly, the hydraulic oil pressure pushes the toothed filling block 261 and the fixing ring 223 to move axially toward the front cover 24, so that the three are tightly pressed against the front thrust ball bearing 222; the other side of the front thrust ball bearing 222 is tightly pressed against the front cover 24, and the synchronous support 27 is pressed against the rear cover 25, completing the axial positioning and sealing of the driven wheel side.

[0045] This embodiment ensures that the effective meshing width of the driving and driven wheels is always equal through precise axial dimension design: the sum of the widths of the toothed filling block 271, the fixing ring 215, and the rear thrust ball bearing 214 is precisely matched with the width of the support 27; the sum of the widths of the toothed filling block 261, the fixing ring 223, and the front thrust ball bearing 222 is completely consistent with the width of the support 26.

[0046] Under the self-tightening action of hydraulic oil pressure, each component fits tightly along the axial direction. The above-mentioned dimensional adaptation relationship is transformed into a precise correspondence of the effective meshing tooth width of the driving and driven wheels, avoiding misalignment of the meshing width due to axial clearance or component displacement, and ultimately achieving stable displacement of the gear pump under normal working conditions.

[0047] If the displacement needs to be adjusted in the same direction, the above displacement adjustment process can be directly used to achieve continuous increase or decrease of displacement without additional operation; if reverse displacement adjustment is required, the adjustment drive component must first be returned to its initial state through a reset process, and then the adjustment process must be restarted from the initial position. The specific reset and reverse adjustment processes are as follows: The drive shaft 21 rotates continuously along the ω direction shown in the figure. This rotation triggers the unlocking mechanism of the adjustment drive component. The rotational power of the drive shaft 21 is transmitted to the lead screw 23, which drives the lead screw bushing 233 to rotate synchronously; the magnetic material at the end of the T-key 232 rotates with the lead screw bushing 233, gradually disengaging from the serrated top locking position of the inner ring 2341 of the one-way bearing 234, thus releasing the magnetic attraction constraint between the two.

[0048] When the T-key 232 is completely disengaged from the locked position, the lead screw bushing 233 loses its circumferential limit, and the torsion spring 236 sleeved at the end of the lead screw 23 releases the pre-stored elastic restoring force, driving the lead screw 23 to rotate in the opposite direction; since the lead screw bushing 233 is fixed to the lead screw 23, the lead screw bushing 233 resets and rotates synchronously with the lead screw 23.

[0049] The rotational motion of the lead screw 23 is converted into the axial movement of the moving block 231 through the trapezoidal thread. The moving block 231 drives the T-key 232 and the fixing ring 215 to move axially towards the rear end cover 25. The toothed filling block 271 retracts inward along the toothed groove of the drive shaft 21 under the pull of the fixing ring 215, and the toothed filling block 261 retracts synchronously with the driven shaft 22.

[0050] During this process, the end of the T-key 232 contacts the serrated inclined surface of the inner ring 2341 of the one-way bearing 234. The continuous axial movement causes the end of the T-key 232 to press against the inclined surface and drive the inner ring 2341 of the one-way bearing 234 to rotate until the T-key 232 returns to its initial position, the gear pump returns to its initial displacement position, and the reset process is completed.

[0051] After reset, reverse displacement adjustment can be initiated, following the same procedure as initial displacement adjustment: The drive shaft 21 rotates along the ω direction, one-way bearing 252 is switched to the locked state, and one-way bearing 234 is in a free-rotating state, providing a channel for power transmission. The rotational power of the drive shaft 21 drives the lead screw 23 to rotate synchronously, and the moving block 231 moves axially towards the target direction, driving the fixed ring 215 and the toothed filling block 271 to slide via the T-key 232, changing the effective meshing tooth width. The toothed filling block 261 moves synchronously and adaptively with the driven shaft 22, maintaining a match with the effective meshing tooth width of the drive wheel. After adjustment to the target displacement, one-way bearing 234 switches to the locked state, working in conjunction with the magnetic attraction of the T-key 232 and the self-locking characteristics of the trapezoidal thread to lock the position, and the torsion spring 236 completes energy storage.

[0052] The above embodiments are merely illustrative of the technical solutions of the present invention and are not intended to limit it. Anyone skilled in the art can modify or alter the above embodiments without departing from the spirit and scope of the present invention. Therefore, all equivalent modifications or alterations made by those skilled in the art without departing from the spirit and technical concept disclosed in the present invention should still be covered by the claims of the present invention.

Claims

1. A continuously variable gear pump characterized by, include: The housing (10) has a water inlet on its surface that penetrates the side of the housing (10); A power component (20) is disposed inside the housing (10). The power component (20) includes a driven shaft (22) and a drive shaft (21) with one end extending through the outside of the housing (10). The drive shaft (21) and the driven shaft (22) are integrally formed with meshing gears (211). The water inlet faces the meshing part of the gears (211). A one-way bearing (234) is fixed at the end of the drive shaft (21). A lead screw (23) is fixed on the inner side of the screw (23), and a moving block (231) is threaded to the outer side of the lead screw (23). A sealing component is provided between the moving block (231) and the gear (211). A one-way bearing (252) fixed to the housing (10) is connected to the outer side of the other end of the lead screw (23). A torsion spring (236) is embedded at the end of the lead screw (23). The rotation direction of the one-way bearing (234) is opposite to that of the one-way bearing (252).

2. A continuously variable gear pump according to claim 1, characterized in that: A front cover (24) is provided on the side of the housing (10) near the end of the drive shaft (21) that protrudes outward. A front sliding bearing (212) and a front sliding bearing (221) are provided inside the front cover (24). The ends of the drive shaft (21) and the driven shaft (22) are inserted into the front sliding bearing (212) and the front sliding bearing (221). A front thrust ball bearing (222) and a support (26) are provided on the outside of the front sliding bearing (212). The front thrust ball bearing (222) is located between the support (26) and the front cover (24).

3. A continuously variable gear pump according to claim 2, characterised in that: The housing (10) is provided with a rear end cover (25), and the rear end cover (25) is provided with a rear sliding bearing one (213) and a rear sliding bearing two (224). The tail of the drive shaft (21) is inserted into the rear sliding bearing one (213), and the tail of the driven shaft (22) is inserted into the rear sliding bearing two (224). The outer side of the rear sliding bearing two (224) is provided with a support two (27).

4. A continuously variable gear pump according to claim 3, characterized in that: The housing (10) has openings at both ends and an elliptical cavity inside. The two opening sides of the housing (10) are detachably provided with caps (11). The tail of the rear cover (25) is provided with a limit block (251). The tail of the driven shaft (22) is detachably fixed to the limit block (251).

5. A continuously variable gear pump according to claim 3, characterized in that: The sealing component includes a toothed filling block one (261) and a toothed filling block two (271). A circular groove is provided on one side of the support one (26) and the support two (27). The toothed filling block one (261) and the toothed filling block two (271) are disposed in the corresponding circular groove. The toothed filling block one (261) and the toothed filling block two (271) fill the outside of the gear (211) of the drive shaft (21) and the driven shaft (22) respectively and form a seal to separate and form a closed cavity. The water inlet is connected to the closed cavity.

6. A continuously variable gear pump according to claim 5, characterized in that: A retaining ring 2 (223) is provided between the front thrust ball bearing (222) and the first toothed filling block (261). The retaining ring 2 (223) is fixed with a pin of the same number as the first toothed filling block (261) on the side near the first toothed filling block (261). The pin is inserted into the interior of the first toothed filling block (261). A rear thrust ball bearing (214) is provided on the outside of the first rear sliding bearing (213). The rear thrust ball bearing (214) fits against the rear end cover (25). A retaining ring 1 (215) is provided between the rear thrust ball bearing (214) and the second toothed filling block (271). The retaining ring 1 (215) is fixed with a pin of the same number as the second toothed filling block (271) on the side near the second toothed filling block (271). The pin is inserted into the interior of the second toothed filling block (271).

7. A continuously variable gear pump according to claim 1, characterized in that: The housing (10) is provided with a bearing support (235) inside. The lead screw (23) includes a rod body (2301). The end of the rod body (2301) away from the drive shaft (21) is provided with a rear groove (2302). The torsion spring (236) is provided inside the rear groove (2302). The one-way bearing (234) is provided inside the bearing support (235). The tail of the drive shaft (21) passes through the one-way bearing (234) and is inserted into the bearing support (235). One end of the torsion spring (236) is detachably fixed to the rear groove (2302), and the other end of the torsion spring (236) is detachably fixed to the inner wall of the bearing support (235).

8. A continuously variable gear pump according to any one of claims 1-7, characterized in that: The inner wall of the one-way bearing (234) is provided with a serrated groove (2344). The drive shaft (21) is fixed with a lead screw bushing (233) on the outer side of the end of the one-way bearing (234). The outer side of the lead screw bushing (233) is provided with a keyway (2331). A T-key (232) is provided between the keyway (2331) and the serrated groove (2344). The end of the T-key (232) inserted into the inner side of the keyway (2331) and the serrated groove (2344) is made of magnetic material. The opening of the serrated groove (2344) faces the moving block (231).

9. A continuously variable gear pump according to claim 8, characterized in that: The one-way bearing (234) includes an outer ring (2343), a roller cage (2342) disposed inside the outer ring (2343), and an inner ring (2341) disposed inside the roller cage (2342). The serrated groove (2344) is formed on the inner wall of the inner ring (2341).

10. A continuously variable gear pump according to claim 8, characterized in that: The movable block (231) has an annular groove on the side near the one-way bearing (234), and the other end of the T-key (2331) is inserted into the annular groove.

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