Hydraulic energy storage and strong drive elevator

Abstract

The utility model discloses a kind of hydraulic energy storage strong drive elevators, including strong drive system, several steel wire ropes and elevator car;Strong drive system includes hydraulic drive device, several reels, one-way power transmission system, travelling crane system, hydraulic variable pump and hydraulic accumulator;First support is fixed on travelling crane system, reel is rotatably installed on first support;Hydraulic drive device drives reel and travelling crane driving sprocket rotation;One end of one-way power transmission system is connected with reel, the other end is connected with hydraulic variable pump, when elevator car descends, reel drives hydraulic variable pump by one-way power transmission system;Hydraulic accumulator is connected with hydraulic drive device, hydraulic variable pump by high-pressure oil pipe;Each steel wire rope corresponds a reel, and one end thereof is connected with reel, and the other end thereof is connected with elevator car.The utility model converts the gravitational potential energy of elevator descent into hydraulic energy by one-way power transmission system, hydraulic variable pump and hydraulic accumulator, and supplies hydraulic drive device.

Description

Technical Field

[0001] This utility model belongs to the field of elevator technology, and in particular relates to a hydraulic energy storage forced drive elevator. Background Technology

[0002] Since the mandatory implementation of the "General Standard for Barrier-Free Construction and Municipal Engineering" (GB 55019-2021) on April 1, 2022, and the "Residential Project Standard" (GB 55038-2025) on May 1, 2025, the following regulations have been clearly stipulated: For newly constructed residential buildings with four or more floors, or residential buildings where the floor level of the entrance is more than 9 meters above the outdoor design ground level, each residential unit must have at least one elevator, and at least one of these elevators must be capable of accommodating a stretcher; for residential buildings with twelve or more floors, or residential buildings where the entrance floor height exceeds 33 meters, each unit should have at least two elevators, with at least one capable of accommodating a stretcher and the other a fire elevator. Stretcher elevators must meet one of two size requirements: wide car: depth ≥ 1.50m, width ≥ 1.60m; deep car: depth ≥ 2.10m, width ≥ 1.10m. By utilizing the diagonal space of the elevator car, a standard scoop stretcher (approximately 1.8m x 0.45m) can be accommodated in a 1.5m x 1.6m car.

[0003] Prior to this, almost all buildings used counterweight traction elevators, the common dimensions of which are shown in the table below (taking a machine room as an example): 800 kg 1900×2100mm 1350×1400mm 1000 kg 2200×2100mm 1600×1400mm The data above shows that a 1000 kg elevator is only close to the standard, while an 800 kg elevator is completely inadequate. With the arrival of an aging society, the actual demand for stretcher elevators is also increasing, and we cannot ignore the elderly living in older buildings. Summary of the Invention

[0004] The purpose of this utility model is to provide a hydraulic energy storage forced drive elevator to address the shortcomings of the existing technology.

[0005] The purpose of this utility model is achieved through the following technical solution: a hydraulic energy storage forced drive elevator, including a forced drive system, several steel wire ropes and an elevator car; The forced drive system includes a hydraulic drive unit, several drums, a one-way power transmission system, a traveling system, a hydraulic variable pump, and a hydraulic accumulator; the traveling system includes a traveling trolley, on which a first bracket is fixed, and the drums are rotatably mounted on the first bracket; The hydraulic drive unit is equipped with a one-way bearing. When the elevator goes up, the hydraulic drive unit simultaneously drives the drum to rotate forward and the trolley to move forward; when the elevator goes down, the drum rotates in reverse and drives the trolley to move in the opposite direction. The one-way power transmission system is equipped with a one-way clutch. One end of the one-way power transmission system is connected to the drum, and the other end is connected to the hydraulic variable pump. When the elevator car descends, the drum drives the hydraulic variable pump through the one-way power transmission system. The hydraulic accumulator is connected to the hydraulic drive device and the hydraulic variable pump through a high-pressure oil pipe. Each wire rope corresponds to a drum, with one end connected to the drum and the other end connected to the elevator car.

[0006] Furthermore, the traveling system includes a traveling system chassis, on which a linear guide rail is placed and a traveling nut is provided, and a traveling vehicle is placed on the linear guide rail; a traveling screw sprocket is fixed on the traveling screw, the traveling screw is screwed into the traveling nut and installed on the traveling vehicle, and the traveling screw sprocket is connected to the traveling vehicle drive sprocket through a chain; a first bracket is fixed on the traveling vehicle. It also includes a brake motor for driving the hydraulic variable pump.

[0007] Furthermore, several reels are connected in series and / or in parallel; When several reels are connected in series, the hydraulic drive device includes: The hydraulic variable motor, clutch-type planetary gear, first gear and fourth gear; the output shaft of the hydraulic variable motor is connected to the clutch-type planetary gear, the clutch-type planetary gear is connected to the first gear, the first gear and the fourth gear mesh, several drums and the fourth gear are fixed on the first drive shaft, and the first drive shaft is rotatably mounted on the first bracket; When several reels are connected in parallel, or in series and parallel, the hydraulic drive device includes: The system includes a hydraulic variable displacement motor, a clutch-type planetary gear, a first gear, a third gear, and a fourth gear. The output shaft of the hydraulic variable displacement motor is connected to the clutch-type planetary gear, which is connected to the first gear. The first gear simultaneously meshes with the third and fourth gears. At least one drum and the fourth gear are fixed on a first drive shaft, which is rotatably mounted on a first bracket. The remaining drums and the third gear are fixed on a second drive shaft, which is rotatably mounted on the first bracket.

[0008] Furthermore, the clutch-type planetary gear includes an input-side planetary gear set and an output-side planetary gear set; the gear ring in the input-side planetary gear set is provided with a gear ring shaft, and a first one-way bearing is sleeved on the gear ring shaft; the outer ring of the first one-way bearing is fixed, and the inner ring is fixed on the gear ring shaft of the gear ring. The first sun gear axle in the input-side planetary gear set is connected to the output shaft of the hydraulic variable motor, and the second planet carrier in the output-side planetary gear set is connected to the third drive shaft. The drive sprocket and the first gear are mounted on the third drive shaft and rotate with the third drive shaft.

[0009] Furthermore, the unidirectional power transmission system includes a speed-coupled planetary gear and a second gear; The rotational speed coupling planetary gear includes an input-side planetary gear set and an output-side planetary gear set; the third sun gear shaft of the input-side planetary gear set is connected to the planet carrier of the output-side planetary gear set via a first one-way clutch, the outer ring of the first one-way clutch is fixed to the third sun gear shaft of the input-side planetary gear set, and the inner ring is fixed to the planet carrier of the output-side planetary gear set; a second one-way bearing is installed on the planet carrier of the output-side planetary gear set. The third drive shaft is connected to the planet carrier of the input-side planetary gear set, and the sun gear of the output-side planetary gear set is connected to the output shaft of the brake motor. The sun gear shaft of the output-side planetary gear set or the output shaft of the brake motor is equipped with a third one-way bearing. The fourth gear ring of the output-side planetary gear set has external teeth, which mesh with the second gear. The second gear is connected to the input shaft of the hydraulic variable pump.

[0010] Furthermore, the input-side planetary gear set and output-side planetary gear set in the clutch-type planetary gear set, as well as the input-side planetary gear set and output-side planetary gear set in the speed-coupled planetary gear set, are single-stage or multi-stage planetary gear sets.

[0011] Furthermore, it also includes a wire rope tension equalizer, with one wire rope tension equalizer corresponding to each wire rope; The wire rope tension equalizer includes a cylinder body, inside which a metal corrugated disc is fixed, forming a sealed cavity filled with a shear-thickening fluid or hydraulic oil. The cylinder body has a connecting port and an exhaust port, which communicate with the cavity. Several connecting ports of the wire rope tension equalizers are connected in series via hydraulic connecting pipes and hydraulic damping holes. An inner cylinder sleeve is fitted into the cylinder body, and a piston is fitted into the inner cylinder sleeve. The cavity formed between the metal corrugated disc, the inner cylinder sleeve, and the piston is filled with single-sized micro steel balls. A ball seat is provided at the bottom of the piston, and a protrusion is provided on the lever shaft, which abuts against the ball seat. One end of the lever shaft has a through hole and is rotatably fitted onto a fixed support, while the other end is fixed with a wire rope. The cylinder body is fixed on a second bracket, and both the second bracket and the fixed support are fixed to the elevator car.

[0012] Furthermore, a through hole is also provided at the other end of the lever shaft for installing a coarse adjustment bolt; the upper part of the coarse adjustment bolt is connected to a wire rope, and the lower part is screwed into a nut.

[0013] Furthermore, the surface of the metal corrugated disk is covered with a liner; the surface of the piston is covered with a bushing.

[0014] Furthermore, it also includes at least one normally closed brake device, which is mounted on the first drive shaft and / or the second drive shaft.

[0015] The beneficial effects of this utility model are: the previous building used a counterweight traction elevator to be transformed into a hydraulic energy storage forced drive elevator of this utility model, so that the net size of the car can accommodate a stretcher. Multiple reels are connected in series and parallel to meet the space requirements of the existing computer room. Extend the service life of steel wire ropes; The gravitational potential energy of the elevator's descent is converted into hydraulic energy through a one-way power transmission system and a hydraulic variable pump, and then stored in a hydraulic accumulator to supply the hydraulic drive device. One stage of the clutch-type planetary gear is designed to rotate only in one direction. When the variable motor is working, the aforementioned external gear ring is locked in the forward rotation, and the power output is sent to the drum to lift the elevator. When the elevator descends and drives the planetary carrier to reverse, the external gear ring is released in the reverse rotation, the planetary gear system is decoupled, and the variable motor will not be affected by the reverse rotation.

[0016] The sun gear of the input-side planetary set of the speed-coupled planetary gear is connected to the planet carrier of the output-side planetary set via a one-way clutch. Due to this one-way clutch, when the drum rotates forward (elevator ascending) or is stationary, the output side of the speed-coupled planetary gear is independent and unaffected by the drum. Furthermore, both the planet carrier and sun gear (or brake motor) of the output-side planetary set are equipped with one-way bearings. The sun gear is only allowed to rotate forward, not backward. The brake motor drives the sun gear to rotate forward. Because the one-way bearing on the planet carrier prohibits forward rotation, the sun gear ultimately drives the external gear ring to rotate backward, keeping the variable pump within its rated speed range. At this time, the variable pump's operation is twofold: firstly, to replenish the hydraulic losses of the accumulator; and more importantly, to pre-maintain the speed of the hydraulic variable pump within its rated operating range to prevent efficiency collapse and loss of control, and to accept planet carrier reversal at any time. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 A schematic diagram of a hydraulic energy storage forced drive elevator structure provided for an embodiment of this utility model; Figure 2 A schematic diagram of a forced drive system structure provided for an embodiment of this utility model; Figure 3 A schematic diagram of a vehicle system chassis structure provided for an embodiment of this utility model; Figure 4 A schematic diagram of a crane and hydraulic drive device provided for an embodiment of this utility model; Figure 5 A schematic diagram of the transmission structure of a hydraulic drive device provided for an embodiment of this utility model; Figure 6A schematic diagram of a traveling double-row drum structure provided for an embodiment of this utility model; Figure 7 A cross-sectional schematic diagram of a clutch-type planetary gear provided for an embodiment of this utility model; Figure 8 A cross-sectional schematic diagram of a speed-coupled planetary gear provided for an embodiment of this utility model; Figure 9 A schematic diagram of a wire rope tension equalizer system provided for an embodiment of this utility model; Figure 10 A schematic diagram of a single wire rope tension equalizer provided in an embodiment of this utility model; Figure 11 A cross-sectional schematic diagram of a wire rope tension equalizer provided for an embodiment of this utility model; Figure 12 A schematic diagram of a metal corrugated disk structure provided for an embodiment of this utility model; Figure 13 A schematic diagram of a forced drive system with a bracket provided for an embodiment of this utility model; Figure 14 An elevator running speed curve is provided for an embodiment of this utility model. Detailed Implementation

[0019] The present invention will now be described in detail with reference to the accompanying drawings. Unless otherwise specified, the features of the following embodiments and implementations can be combined with each other.

[0020] This utility model relates to a hydraulic energy storage forced drive elevator, see [link to relevant documentation]. Figure 1 It includes a forced drive system 100, several steel wire ropes 200 and an elevator car 300; See Figure 2 and Figure 13 The forced drive system 100 includes a hydraulic drive unit, several drums 116, a one-way power transmission system, a traveling system, a hydraulic variable pump 113, and a hydraulic accumulator. The crane system includes a crane 103, on which a first bracket 122 is fixed, and a drum 116 is rotatably mounted on the first bracket 122; When the elevator ascends, the hydraulic drive unit simultaneously drives the drum 116 to rotate forward and the trolley 103 to move forward; when the elevator descends, the drum 116 reverses, driving the trolley 103 to move in the opposite direction; a one-way bearing is installed in the hydraulic drive unit. The function of this one-way bearing is as follows: when the elevator ascends, the one-way bearing is locked to transmit the torque output by the hydraulic drive unit (hydraulic variable motor), and the drum rotates, i.e., it rotates forward (when the elevator ascends, the drum rotates forward); when the elevator descends, the drum 116 rotates (reverses), and the one-way bearing can rotate, so that the hydraulic drive unit (output shaft of the hydraulic variable motor) is not affected.

[0021] When the elevator descends, the drum 116 reverses, driving the trolley 103 to move in the opposite direction, that is, converting the rotational motion of the drum 116 into linear motion: a gear coaxial with the drum is provided, and the screw moves relative to the nut through gear transmission and / or chain transmission (the screw is installed on the trolley 103, and the nut is fixed), so as to realize the reverse movement of the trolley 103.

[0022] It should be noted that when the elevator ascends, the hydraulic drive device simultaneously drives the drum 116 to rotate forward and the trolley 103 to move forward, including: the hydraulic drive device (which includes a reducer) directly drives the drum 116 to rotate forward, and simultaneously drives the screw to move relative to the nut through gear transmission and / or chain transmission, causing the trolley 103 to move forward; or the hydraulic drive device directly drives the drum 116 to rotate forward, in which case the drum 116 drives the screw to move relative to the nut through gear transmission and / or chain transmission, causing the trolley 103 to move forward; wherein, when the hydraulic drive device drives the drum 116 to rotate forward, and the drum 116 drives the trolley 103 to move forward through the transmission system, the forward movement of the trolley 103 should also be understood as being driven by the hydraulic drive device.

[0023] One end of the unidirectional power transmission system is connected to the drum 116, and the other end is connected to the hydraulic variable pump 113. When the elevator car descends, the drum 116 drives the hydraulic variable pump 113 through the unidirectional power transmission system. The hydraulic accumulator is connected to the hydraulic drive device and the hydraulic variable pump 113 through a high-pressure oil pipe. A unidirectional clutch is installed in the unidirectional power transmission system. The function of the unidirectional clutch is as follows: when the elevator descends, the drum 116 reverses, and the unidirectional clutch locks (at this time, the entire unidirectional clutch rotates), transmitting the torque of the drum 116 to the hydraulic variable pump 113. When the elevator ascends, the drum 116 rotates forward, and the unidirectional clutch is unlocked and cannot transmit torque, thus realizing unidirectional power transmission.

[0024] Each wire rope 200 corresponds to a drum 116, with one end connected to the drum 116 and the other end connected to the elevator car 300.

[0025] In one embodiment, see Figure 3 and Figure 4The gantry system includes a gantry system chassis 101, on which a linear guide rail 102 is placed and a gantry nut 101-1 is provided. A gantry 103 is placed on the linear guide rail 102. A gantry screw sprocket 105 is fixed on a gantry screw 104. The gantry screw 104 is screwed onto the gantry nut 101-1 and installed on the gantry 103. The gantry screw sprocket 105 is connected to the gantry drive sprocket 106 via a chain. When the elevator rises, the hydraulic drive device drives the drum 116 to rotate (forward) and simultaneously drives the gantry drive sprocket 106 to rotate (forward), causing the gantry 103 to move forward (defined as the positive direction when the elevator rises). The drum 116 moves accordingly. When the elevator descends, the drum rotates (reverse), driving the gantry drive sprocket 106 to rotate (reverse), causing the gantry 103 to move in the opposite direction. The drum drives the gantry drive sprocket 106 to rotate in the following ways: The crane drive sprocket 106 is fixed on the same shaft as the first gear 107; a gear (i.e., the fourth gear 115, which is fixed on the same shaft as the drum 116) is provided on the same shaft as the drum 116, and this gear meshes with the crane drive sprocket 106.

[0026] In one embodiment, a brake motor 111 is also included, the output shaft of which is connected to the sun gear of the output planetary gear set of the speed-coupled planetary gear (110) for driving the hydraulic variable pump 113.

[0027] In one embodiment, a plurality of rolls 116 are connected in series and / or in parallel; When several drums 116 are connected in series, the hydraulic drive device includes: The system includes a hydraulic variable displacement motor 109, a clutch-type planetary gear 108, a first gear 107, and a fourth gear 115. The output shaft of the hydraulic variable displacement motor 109 is connected to the clutch-type planetary gear 108, which is connected to the first gear 107. The first gear 107 and the fourth gear 115 mesh. Several drums 116 and the fourth gear 115 are fixed on a first drive shaft 118, which is rotatably mounted on a first bracket 122. When several rolls 116 are connected in parallel, or in series and parallel, see [reference needed]. Figure 5 and Figure 6 The hydraulic drive unit includes: The system includes a hydraulic variable displacement motor 109, a clutch-type planetary gear 108, a first gear 107, a third gear 114, and a fourth gear 115, with the third gear 114 and the fourth gear 115 having the same dimensions. The output shaft of the hydraulic variable displacement motor 109 is connected to the clutch-type planetary gear 108, which is connected to the first gear 107. The first gear 107 simultaneously meshes with the third gear 114 and the fourth gear 115. At least one drum 116 and the fourth gear 115 are fixed on a first drive shaft 118, which is rotatably mounted on a first bracket 122. The remaining drums 116 and the third gear 114 are fixed on a second drive shaft 119, which is rotatably mounted on the first bracket 122.

[0028] The hydraulic accumulator is connected to the hydraulic variable motor 109 and hydraulic variable pump 113 in the hydraulic drive device via a high-pressure oil pipe.

[0029] In one embodiment, a first housing 108-8 is included, which encloses and supports the clutch-type planetary gear 108; see also Figure 7 The clutch-type planetary gear 108 includes an input-side planetary gear set and an output-side planetary gear set; both the input-side and output-side planetary gear sets include a sun gear, several planet gears, and a planet carrier. The input-side planetary gear set includes a first sun gear, several first planet gears 108-2, a first planet carrier 108-3, and a first gear ring 108-4; the first sun gear meshes with several first planet gears 108-2, and the several first planet gears 108-2 are mounted on the first planet carrier 108-3 and mesh with the internal teeth of the first gear ring 108-4.

[0030] The first sun gear is fixed to a first sun gear shaft 108-1 (i.e., the input shaft). At least one bearing (deep groove bearing) is fitted on the first sun gear shaft 108-1, with its outer ring fixed to the first outer casing 108-8 and its inner ring fixed to the first sun gear shaft 108-1. Planetary carriers 108-3 have planetary carrier shafts on both sides, with at least one bearing (deep groove bearing) fitted on each side. The outer ring of each bearing is fixed to the first outer casing 108-8, and its inner ring is fixed to the planetary carrier shaft. The first gear ring 1... 08-4 has gear ring shafts on both sides, and at least one bearing (deep groove bearing) is fitted on each gear ring shaft. The outer ring of the bearing is fixed to the first housing 108-8, and the inner ring is fixed to the gear ring shaft. At least one gear ring shaft has a first one-way bearing 108-7 fitted on it. The outer ring of the first one-way bearing 108-7 is fixed to the first housing 108-8, and the inner ring is fixed to the gear ring shaft. The first sun gear shaft 108-1 is connected to the output shaft of the hydraulic variable motor 109 to drive the sun gear of the input planetary gear set to rotate.

[0031] The function of the first one-way bearing 108-7 is as follows: when the elevator is ascending, the first gear ring 108-4 controlled by the first one-way bearing 108-7 is locked, and the output power of the hydraulic variable motor 109 can drive the drum 116 through the clutch planetary gear 108; when the elevator is descending, the output shaft of the clutch planetary gear 108 rotates in a different direction, and the first gear ring 108-4 controlled by the first one-way bearing 108-7 rotates freely, so the output shaft of the hydraulic variable motor 109 is not affected by "backward drag". Furthermore, a one-way bearing can be added to the output shaft of the hydraulic variable motor 109 (the inner ring of the one-way bearing is fitted onto and fixed to the output shaft of the hydraulic variable motor 109, and the outer ring is fixed to the first sun gear axle 108-1), thereby improving reliability.

[0032] The output-side planetary gear set includes a second sun gear, several second planet gears, a second planet carrier 108-6 (i.e., the output shaft), and a second ring gear 108-5. The second sun gear is mounted on the first planet carrier 108-3. Specifically, the second sun gear is fitted onto the planet carrier shaft facing the output side of the first planet carrier 108-3 and fixed (or the planet carrier shaft is provided with a spline, thereby driving the second sun gear to rotate). Several second planet gears are mounted on the second planet carrier 108-6 and mesh with the internal teeth of the second sun gear and the second ring gear 108-5. The second ring gear is fixed (the outer side of the second ring gear is fixed to the first outer casing 108-8).

[0033] The working principle of the clutch-type planetary gear 108 is as follows: When the elevator rises, the hydraulic variable motor 109 drives the first sun gear to rotate, thereby driving the first planet gear 108-2 and the first planet carrier 108-3 to rotate. At this time, the first gear ring 108-4 is locked by the first one-way clutch bearing 108-7. The rotation of the first planet carrier 108-3 then drives the second sun gear, the second planet gear, and the second planet carrier 108-6 to rotate in sequence. The rotation of the second planet carrier 108-6 drives the drum 116 to work. When the elevator descends, the first gear ring 108-4 can rotate freely, and the output shaft of the hydraulic variable motor 109 is not affected by the "backward drag".

[0034] The clutch-type planetary gear 108 is a reduction gear set. In one embodiment, the reduction gear set is a two-stage planetary gear set with transmission ratios of 5 and 6.

[0035] In one embodiment, a second housing 110-8 is included, which encloses and supports the rotationally coupled planetary gear 110 and the second gear 112; see also Figure 8 The rotational speed coupling planetary gear 110 includes an input-side planetary gear set and an output-side planetary gear set; both the input-side and output-side planetary gear sets include a sun gear, several planet gears, and a planet carrier. The input-side planetary gear set includes a third sun gear, several third planet gears, a third planet carrier, and a third ring gear (not shown in the figure). The third sun gear meshes with several third planet gears. Several third planet gears are mounted on the third planet carrier and mesh with the inner ring of the third ring gear. The third ring gear is fixed (the outer side of the third ring gear is fixed to the second housing 110-8). The third sun gear has a third sun gear shaft 110-1, on which at least one bearing (deep groove bearing) is fitted. Its outer ring is fixed to the second housing 110-8, and its inner ring is fixed to the third sun gear shaft 110-1. The third planet carrier is connected to the third drive shaft 120. The output-side planetary gear set includes a fourth sun gear 110-5, several fourth planet gears 110-4, a fourth planet carrier 110-3, and a fourth ring gear 110-6. The fourth planet carrier 110-3 is connected to the third sun gear shaft 110-1 via a first one-way clutch 110-2. The outer ring of the first one-way clutch 110-2 is fixed to the third sun gear shaft 110-1, and the inner ring is fixed to the planet carrier 110-3 of the output-side planetary gear set. The fourth sun gear 110-5 is connected to several fourth planet gears 110-4. Planetary gears 110-4 mesh; several fourth planetary gears 110-4 are mounted on the fourth planetary carrier 110-3 and mesh with the internal teeth of the fourth gear ring 110-6. The fourth gear ring 110-6 also has external teeth, which mesh with the second gear 112. The second gear 112 is fitted onto and fixed to the fourth drive shaft 121; the fourth drive shaft 121 is fitted with at least two bearings (deep groove bearings), the outer ring of which is fixed to the second housing 110-8, and the inner ring is fixed to the fourth drive shaft 121, and positioned... On both sides of the second gear 112; the fourth drive shaft 121 is connected to the hydraulic variable pump 113; planetary carrier shafts are provided on both sides of the fourth planetary carrier 110-3, and at least one bearing (deep groove bearing) is fitted on each planetary carrier shaft on both sides. The outer ring of the bearing is fixed to the second housing 110-8, and the inner ring is fixed to the planetary carrier shaft. At least one of the planetary carrier shafts is fitted with a second one-way bearing 110-7. The outer ring of the second one-way bearing 110-7 is fixed to the second housing 110-8, and the inner ring is fixed to the planetary carrier shaft. Fixed; the fourth gear ring 110-6 has gear ring shafts on both sides, and each gear ring shaft has at least one bearing (deep groove bearing) fitted on it. Its outer ring is fixed to the second housing 110-8, and its inner ring is fixed to the gear ring shaft; the fourth sun gear 110-5 has a fourth sun gear shaft 110-9 (i.e., input shaft), and the fourth sun gear shaft 110-9 has at least one bearing (deep groove bearing) fitted on it. Its outer ring is fixed to the second housing 110-8, and its inner ring is fixed to the fourth sun gear shaft 110-9. The fourth sun gear shaft 110-9 is connected to the output shaft of the brake motor 111. The sun gear shaft of the output planetary gear set or the output shaft of the brake motor 111 is equipped with a third one-way bearing (not shown in the figure). Preferably, the output shaft of the brake motor 111 is equipped with a third one-way bearing.

[0036] Working principle of speed-coupled planetary gear 110: When the elevator descends, the drum 116 rotates, driving the first gear 107 to rotate, and the third drive shaft 120 rotates accordingly, thereby driving the third planetary carrier to rotate; the third ring gear is fixed, and the third planetary carrier drives the third sun gear to rotate (the rotation direction of the third sun gear is defined as reverse when the elevator descends). At this time, the first one-way clutch 110-2 is locked (the entire first one-way clutch 110-2 rotates in reverse) and transmits torque. The second one-way bearing 110-7 can rotate in reverse. The third sun gear drives the fourth planetary carrier 110-3 to rotate in reverse. At the beginning, the fourth sun gear is driven to rotate in the forward direction by the brake motor (when the speed reaches the set value, the brake motor is de-energized and fixed, and the sun gear is also fixed in linkage). The fourth planetary gear 110-4 also rotates in the reverse direction (its rotation speed is the coupling acceleration effect of the reverse rotation speed of the fourth planetary carrier and the forward rotation speed of the fourth sun gear), thereby driving the fourth ring gear 110-6 to rotate in the reverse direction. The fourth ring gear 110-6 drives the second gear 112 to rotate in the forward direction, thereby driving the hydraulic variable pump 113. When the elevator ascends, the third sun gear rotates in the forward direction, the first one-way clutch 110-2 is unlocked, and the output-side planetary gear set can work independently. Because the second one-way bearing 110-7 of the fourth planetary carrier 110-3 restricts its forward rotation, the brake motor 111 drives the fourth sun gear 110-5 to rotate in the forward direction, which in turn drives the fourth planetary gear 110-4 to rotate in the reverse direction, thereby driving the fourth gear ring 110-6 to rotate in the reverse direction, which in turn drives the second gear 112 to rotate in the forward direction, thereby driving the hydraulic variable pump 113.

[0037] The speed-coupled planetary gear 110 is a speed-increasing gear set. In one embodiment, the speed-increasing gear set is a three-stage planetary gear set. The first two stages are called the input side, and the speed-increasing ratio of each stage is 4, with a total speed-increasing ratio of 16. The last stage is called the output side, and the ratio of the number of teeth of the ring gear to the number of teeth of the sun gear is 6.

[0038] In summary, when the hydraulic variable motor 109 acts as the power source, power is transmitted unidirectionally to the drum 116, driving the elevator upwards. This does not affect the operation of the hydraulic variable pump 113 and the brake motor 111. Conversely, when the elevator descends and the drum 116 acts as the power source, power is transmitted unidirectionally to the hydraulic variable pump 113, which stores potential energy. This also does not affect the stopping condition of the hydraulic variable motor 109. The brake motor 111 assists the hydraulic variable pump 113 during the elevator's descent phase, or independently drives the hydraulic variable pump 113 during the elevator's stopping (or ascending) phase.

[0039] See Figure 13 It also includes a third housing 123 for enclosing the gears, as well as supporting the hydraulic drive unit, the speed-coupled planetary gear 110, the brake motor 111, and the hydraulic variable pump 113.

[0040] In one embodiment, see Figure 9 It also includes a wire rope tension equalizer 400, with one wire rope tension equalizer 400 corresponding to each wire rope 200. See Figures 10 to 12 The wire rope tension equalizer 400 includes a cylinder body 401, inside which a metal corrugated disc 403 is fixed, forming a sealed cavity. This cavity is filled with a shear-thickening fluid 402 or hydraulic oil (hydraulic oil for standard versions, and a shear-thickening fluid, i.e., a non-Newtonian fluid, for high-end versions). The cylinder body 401 has a connecting port and an exhaust port (the exhaust port is only used to release air during assembly and filling with liquid; it can be closed after assembly), which communicate with the cavity. Several connecting ports of the wire rope tension equalizers 400 are connected via hydraulic connecting pipes. An inner cylinder liner 408 is fitted into the cylinder body 401, and a piston 4... The inner cylinder liner 408 is fitted into the piston 406. The cavity formed between the metal corrugated disc 403, the inner cylinder liner 408, and the piston 406 is filled with single-sized micro steel balls 405. A ball seat 406-1 is provided at the bottom of the piston 406. A protrusion 410-1 is provided on the lever shaft 410, which abuts against the ball seat 406-1. One end of the lever shaft 410 is provided with a through hole and is rotatably fitted onto the fixed support 409. A steel wire rope 200 is fixed at the other end. The cylinder body 401 is fixed on the second bracket 412. Both the second bracket 412 and the fixed support 409 are fixed on the elevator car 300.

[0041] In one embodiment, the inner cylinder liner 408 has a guide ring 408-1 on the side facing the metal bellows disc 403; In one embodiment, the other end of the lever shaft 410 is also provided with a through hole for installing a coarse adjustment bolt 411; the upper part of the coarse adjustment bolt 411 is connected to a wire rope 200, and the lower part is screwed into a nut.

[0042] In one embodiment, the shear thickening fluid 402 is hydraulic oil; other shear thickening fluids may also be selected, and are not limited here.

[0043] In one embodiment, the surface of the metal corrugated disc 403 is covered with a liner 404; the surface of the piston 406 is covered with a bushing 407. The liner 404 may be made of a high-molecular-weight, low-friction, easily deformable material, and the bushing 407 may be made of materials such as nylon.

[0044] Further explanation: The function of the guide ring 408-1 of the inner cylinder liner 408: Because the deformation capacity of the metal bellows 403 is greater at the center than at the periphery, the guide ring 408-1 is set to constrain the movement of the single-sized micro steel balls 405 towards the center of the metal bellows 403. Simultaneously, because the planar stiffness of the piston 406 is much greater than that of the metal bellows 403, the guide angle should be as shown in the figure. After multiple wire rope tension equalizers 400 are installed on the upper part of the elevator car 300, the hydraulic connection ports of each wire rope tension equalizer 400 are connected into a single unit via hydraulic connecting pipes. During connection, hydraulic damping holes (also known as "hydraulic resistance" or "throttling holes") must be connected in series. The function of the initial adjustment bolt is: During elevator installation, when the elevator car 300 is in a temporary support state, the length of multiple wire ropes can be adjusted by rotating the nut to ensure that the force on each wire rope is as equal as possible in the initial state. The upper and lower limits depend on the degree of deformation of the metal bellows and can be determined based on actual testing.

[0045] This invention addresses both the slow, unbalanced elongation caused by wear and tear on the wire rope and the sudden rope breakage. When the traction force changes slowly, the corrugated disc rises or falls slowly due to the interconnectedness of the pipeline, automatically balancing the pressure and traction force at various points using the principle of communicating vessels. In the event of a rope breakage, the presence of damping orifices prevents a chain reaction of collapse. This invention is particularly advantageous when the internal cavity is filled with a shear-thickening fluid. Shear-thickening fluids are currently used in earthquake-resistant building structures and automotive airbag triggering systems. The innovation of this invention lies in the fact that the corrugated disc and cylinder form a sealed space, avoiding the risk of oil leakage compared to traditional cylinder and piston structures, thus achieving maintenance-free operation. Furthermore, this invention is particularly advantageous for the elevator industry because the cyclic stress during elevator ascent and descent helps maintain higher fluidity in single-particle microspheres, expanding the range of material choices and reducing costs.

[0046] In one embodiment, a normally closed brake device 117 is also included for braking and stopping the entire drive system and thus stopping the operation of all drums 116. The normally closed brake device 117 is mounted on the first drive shaft 118 and / or the second drive shaft 119.

[0047] Regarding the hydraulic accumulator: The core energy storage component of this system is the hydraulic accumulator, which can be installed on the traveling crane 103 or in other suitable locations and connected to the hydraulic variable motor 109 and the hydraulic variable pump 113 via high-pressure oil pipes. Therefore, the specific location of the hydraulic accumulator is not shown in the figure.

[0048] Wire rope service life: Due to the required rope capacity, the forced drive system has to increase the drum diameter (in this case: wire rope diameter 10mm, traction force 8.3% breaking strength, drum diameter 600mm, with rope groove, single-layer winding of wire rope), but this also brings additional life extension to the wire rope. For example, the elevator operation frequency of an 18-story residential building is affected by resident density, elevator-to-household ratio, and peak-hour concentration. Typically, there are 2 elevators serving 4 or 6 households, so a single elevator serves approximately 36-54 or 54-72 households, resulting in an average of 150-300 trips per elevator per day. When a drum system is used, the number of bends in the wire rope during each elevator trip is reduced from 2 times with the traction sheave to 1 time, theoretically increasing the fatigue life by 2 times; and by changing from the friction drive of the traction sheave to the mechanical locking drive of the drum, the frictional loss of the wire rope by the traction sheave rope groove is eliminated. Therefore, the theoretical lifespan of a wire rope can reach 25 to 35 years, which is about 2 to 3 times that of a traditional traction sheave. However, actual replacement should still be based on the number of broken wires or the wear of the diameter.

[0049] Working principle explanation: One reason why forced-drive systems have not been widely adopted is the torque and power matching problem inherent in motor-driven systems. Because forced-drive systems eliminate counterweight balancing, calculations in this case (1000kg load) show that the peak torque of the drum exceeds 6.1 kN.m, and the peak mechanical power exceeds 28 kW. This is the biggest unavoidable challenge when using an electric motor as the prime mover. However, using a hydraulic motor and hydraulic pump combined with hydraulic energy storage technology can take full advantage of the inherent advantages of hydraulic systems, such as high power density, large low-speed torque, and the ability to stagger energy storage and work output.

[0050] 1. Elevator speed target, such as Figure 14 As shown: One embodiment aims to convert an existing elevator into a stretcher elevator. Therefore, the corresponding technical specifications refer to the rigid limits of "GB25198-2010 Medical Elevator Specification": acceleration ≤0.50 m / s², speed ≤1.5 m / s. A seven-segment line scheme is used to set the speed curve.

[0051] 2. The counterweight is eliminated, and the corresponding energy storage function is replaced by a hydraulic accumulator, which converts the gravitational potential energy during the elevator's descent into hydraulic mechanical energy, which is then reused during the ascent.

[0052] 3. During the elevator's lifting phase, a hydraulic variable motor and a proportional valve convert the accumulator's hydraulic pressure into rotational kinetic energy, which is then used to drive the elevator upwards via planetary gear reduction. Speed ​​control is achieved through the combined action of the hydraulic variable motor and the proportional valve (especially during the hydraulic pump's startup phase). Furthermore, one stage of the planetary gear reducer's external gear ring is designed to rotate only in one direction. Taking the hydraulic variable motor's forward rotation input to the sun gear and the planetary carrier's forward rotation output to the drum as an example (this direction setting will be used subsequently): when the variable motor is working, the aforementioned external gear ring is locked in forward rotation, and power is output to the drum, causing the elevator to lift; when the elevator descends, causing the planetary carrier to reverse, the external gear ring is released in reverse, the planetary gear system is decoupled, and the variable motor is unaffected by the reverse rotation.

[0053] 4. During the elevator's descent phase: The drum drives the input planetary carrier of the planetary gear to reverse, and after speed increase, it drives the output planetary carrier to reverse through the first one-way clutch (the first one-way clutch is installed here to reduce the working torque, but it can also be installed in the same position on the front planetary gear set, which is beneficial for reducing the number of linkage parts and reducing mechanical losses, but a one-way clutch with a larger rated torque must be used).

[0054] The mechanical structure of the output side of the "speed-coupled planetary gear" is as follows: The sun gear of the output planetary gear set is connected to a brake motor, which is equipped with a one-way bearing (or the fourth sun gear shaft 110-9 is equipped with a one-way bearing), allowing only forward rotation and not reverse rotation. The planet carrier is connected to the input stage sun gear (including the first one-way clutch). Due to the one-way bearing on its own shaft, the planet carrier is only allowed to rotate in reverse and not forward. The gear ring is connected to a hydraulic variable pump, and the hydraulic variable pump outlet is equipped with a one-way valve, allowing only reverse rotation and not forward rotation. The torque relationship between the sun gear, planet carrier, and external gear ring is T: -(1+K)×T:K×T, where T is the proportional factor and K is the gear ratio (6 in this embodiment).

[0055] Principle description: 1. Due to the presence of the first one-way clutch 110-2, when the drum 116 rotates forward (elevator rises) or is stationary, the output side of the speed coupling planetary gear is in an independent state and is not disturbed by the drum 116.

[0056] 2. When the output side of the speed-coupled planetary gear is in an independent working state, the fourth sun gear 110-5 is driven to rotate forward by the brake motor 111. Because the second one-way bearing 110-7 of the fourth planetary carrier 110-4 prohibits the fourth planetary carrier from rotating forward, the fourth sun gear 110-5 ultimately drives the fourth ring gear 110-6 to rotate in reverse, and keeps the hydraulic variable pump 113 within its rated speed range (500~2000 RPM in this embodiment). At this time, the rotation of the hydraulic variable pump is to replenish the hydraulic accumulator to compensate for hydraulic losses, and more importantly, to maintain the speed of the hydraulic variable pump within its rated working range in advance to prevent the hydraulic variable pump efficiency from collapsing and becoming uncontrollable, and to accept the planetary carrier reversal at any time (i.e., the aforementioned elevator descent). Note: The rated torque of the selected brake motor must be greater than the maximum reflected torque that the elevator's highest load can generate (in this embodiment, an 11 kW 2-pole three-phase asynchronous brake motor with thyristor voltage regulation soft start is selected).

[0057] 3. When the elevator is preparing to descend, the PLC reduces the torque proportional factor T by decreasing the displacement of the hydraulic variable pump according to the actual load of the elevator (see below: Control Method). When the reflected torque of the fourth planetary carrier 110-3 (in reverse direction, provided by the second one-way bearing 110-7) exactly matches the reversing torque to be superimposed, the normally closed brake device 117 is released. At this time, the reversing torque obtained by the fourth planetary carrier 110-3 due to the release of the normally closed brake device 117 replaces the reflected torque previously received by the fourth planetary carrier 110-3. The torque is still balanced, the elevator will not descend, but the second one-way bearing 110-7 is in a floating state.

[0058] 4. The PLC continues to control the hydraulic variable pump to decrease its displacement (T decreases). The fourth planetary carrier 110-3 gradually begins to reverse, and its speed is coupled and superimposed on the fourth ring gear 110-6, increasing the reverse rotation speed of the fourth ring gear 110-6. At this time, the energy flow is as follows: input from the fourth sun gear 110-5 and the fourth planetary carrier 110-3, output from the outer ring gear of the fourth ring gear 110-6, and the combined power of the kinetic energy of the brake motor 111 and the potential energy of the elevator's descent is output to the hydraulic variable pump 113. During this process, due to the decrease in the torque proportional factor T, the motor speed increases slightly but cannot exceed the synchronous speed (magnetic field speed), and the actual output torque will automatically follow the change, i.e., the actual output power decreases.

[0059] 5. As the reverse speed of the fourth planetary carrier 110-3 continues to increase, the brake motor 111 will shut down at an opportune time. The purpose of shutting down is to prevent the speed of the hydraulic variable pump 113 from exceeding the set upper limit. At the moment the brake motor 111 shuts down, since the displacement of the hydraulic variable pump 113 remains unchanged, the torque proportional factor T also remains unchanged. However, the reflected torque on the fourth sun gear 110-5 drives its speed to rapidly decrease until it reaches zero. During this process, the speed of the hydraulic variable pump 113 also decreases rapidly. The braking function of the brake motor 111 needs to achieve a performance balance. On the one hand, the braking must be decisive; on the other hand, the impact effect must be prevented. At the same time, the fourth sun gear 110-5 has a third one-way bearing to prevent reverse rotation as a mechanical safety guarantee.

[0060] 6. After the brake motor 111 is turned off, the hydraulic variable pump 113 is driven independently by the fourth planetary carrier 110-3. At this time, the speed of the hydraulic variable pump 113 is still within the rated range, continuing to efficiently convert potential energy into hydraulic energy.

[0061] 7. Before the elevator reaches its destination, the speed of the fourth planetary carrier 110-3 gradually returns to zero. At this point, you can choose to open the brake motor 111 or not. The reason for not opening it is that the low-speed zone time is less than the lubricating oil film dissipation time of the hydraulic variable pump 113, and the hydraulic variable pump 113 still maintains mechanical efficiency. The reason for opening it is to maintain volumetric efficiency and improve control accuracy.

[0062] The core innovation of this power system lies in its "rotational speed coupling planetary gear." This mechanism ensures the normal operation of the hydraulic variable pump, enabling energy recovery across the entire speed range from 0 to its maximum value during elevator descent. This is the advantage of this system. This solution differs significantly from motor-generated energy recovery methods. The efficiency range of the power generation mode is very narrow, making it difficult to adapt to low-speed stages. Moreover, it requires multiple conversions from mechanical energy to electrical energy to chemical energy and back to electrical energy and mechanical energy, resulting in high losses.

[0063] Control method: 1. Mechanical Locking State: When the normally closed brake device 117 is in the locked state, the support structure of the normally closed brake device 117 receives a torque signal. The PLC can obtain the actual load of the elevator (including the current total static friction of the mechanical system) through this signal, providing a real-time basis for subsequent control.

[0064] 2. Ascending Phase: During the initial ascent phase, the proportional valve of the hydraulic variable motor is the primary controller, with the variable mechanism following suit. After the hydraulic variable motor starts, the variable mechanism controls the output torque, thereby controlling the elevator speed. During the deceleration phase of the hydraulic variable motor, since the transition time is less than the dissipation time of the friction pair oil film, the variable mechanism will continue to operate normally, and the proportional valve does not need to intervene.

[0065] 3. Descent Phase: Based on the pressure signal, the PLC controls the hydraulic variable pump to reach the preset displacement, and simultaneously starts the brake motor (the brake motor's stall torque is greater than the hydraulic variable pump's starting torque). Subsequently, the variable displacement mechanism of the hydraulic variable pump controls the reflected torque, thereby controlling the elevator speed. The PLC will employ both open-loop feedforward control and closed-loop feedback control simultaneously. The feedforward data includes pre-defined speed curves, pump and motor performance curves, and load data provided by pressure sensors. The closed-loop control data comes from the encoder's acquisition and feedback of the actual operating speed and the accumulator pressure sensor.

[0066] 4. Regarding the control method of the brake motor: If the voltage and frequency of the local power grid are relatively stable or the requirements for elevator smoothness are not high, a common three-phase asynchronous brake motor can be used. Otherwise, an industrial frequency converter should be added to control the actual output torque of the brake motor.

[0067] In one embodiment, if a traction elevator with a counterweight is converted into a forced-drive elevator of this utility model, and the space occupied by the counterweight is converted into the car space, the requirements of a stretcher elevator can be met, as shown in the table below: 800 kg 1900×2100mm 1550×1600mm 1000 kg 2200×2100mm 1800×1550mm Analysis of the rope length capacity of the drum: In residential buildings, we generally refer to 4-6 stories (outdoor height within 27 meters) as multi-story buildings, 7-11 stories (outdoor height 28-33 meters) as mid-rise buildings, 9-17 stories (outdoor height 27-54 meters) as Class II high-rise buildings, 9-17 stories (outdoor height 54-100 meters) as Class I high-rise buildings, and those with an outdoor height of over 100 meters as super high-rise buildings. Some people also refer to 7-11 story (outdoor height 28-33 meters) residential buildings solely as mid-rise buildings.

[0068] Taking a typical 11-story building (1 basement level) as an example: Assuming a floor height of 2.9 meters, the total lifting height is 10 × 2.9 + 3.5 = 32.5 meters. With a drum diameter of 0.6 meters, the number of winding turns is 17.24. According to GB 7588-2003 "Safety Code for Elevator Manufacturing and Installation," only one layer of wire rope is allowed on the drum. When the car is completely pressed against the buffer, at least 1.5 turns of wire rope must remain on the drum. The "Safety Regulations for Lifting Machinery" (GB 6067.1-2010) stipulates that single-layer winding drums must have rope grooves machined, with a groove spacing of 1.03 to 1.14 times the wire rope diameter. Drum length: The working rope for an 800 or 1000 kg elevator typically consists of 5 10mm wire ropes. Based on 20 coils (17.24 + 1.5), a rope groove spacing of 10.5 mm, and a drum flange thickness of 12 mm, the total length of 5 drums connected in series is calculated to be 20 × 10.5 × 5 + 12 × 6 = 1122 mm. Analysis: Generally, the width of the machine room for an 800 kg elevator is greater than or equal to 3.3 meters, while for a 1000 kg elevator it is 3.5 meters (3.6 meters is common). Based on the aforementioned drum length calculation, and considering the subsequent power system layout and maintenance access requirements, the machine room space is sufficient.

[0069] Taking a typical 18-story building (2 underground floors) as an example: assuming a floor height of 2.9 meters, the total lifting height would be 17 × 2.9 + 4.2 × 2 = 57.7 meters. (Using the following...) Figure 6 The shown double-row traveling drum has a single drum diameter of 0.6 meters, resulting in 30.61 turns per layer. We'll actually use 33 turns (30.61 + 1.5). The length of the three drums connected in series is approximately 33 × 10.5 × 3 + 12 × 4 ≈ 1100 mm. Adding the approximately 0.35 meter transmission equipment and the approximately 0.33 meter travel distance, the total width occupied is 1.78 meters. Considering the requirements for the support frame and maintenance access, the available space in the machine room is still sufficient.

[0070] The five wire ropes 200, five drums 116, and five wire rope tension equalizers 400 shown in the attached diagram are merely illustrative, and their quantity is not limited; the appropriate quantity can be configured according to the actual situation.

[0071] Other embodiments of this application will readily occur to those skilled in the art upon consideration of the specification and practice of the disclosure herein. This application is intended to cover any variations, uses, or adaptations of this application that follow the general principles of this application and include common knowledge or customary techniques in the art not disclosed herein. The specification and embodiments are to be considered exemplary only.

[0072] It should be understood that this application is not limited to the precise structure described above and shown in the accompanying drawings, and various modifications and changes can be made without departing from its scope.

Claims

1. A hydraulic energy storage forced drive elevator, characterized in that, Includes a forced drive system (100), several steel wire ropes (200) and an elevator car (300). The forced drive system (100) includes a hydraulic drive unit, several drums (116), a one-way power transmission system, a traveling system, a hydraulic variable pump (113), and a hydraulic accumulator; the traveling system includes a traveling vehicle (103), on which a first bracket (122) is fixed, and the drums (116) are rotatably mounted on the first bracket (122); The hydraulic drive unit is equipped with a one-way bearing. When the elevator goes up, the hydraulic drive unit simultaneously drives the drum (116) to rotate forward and the trolley (103) to move forward. When the elevator goes down, the drum (116) reverses and drives the trolley (103) to move in the opposite direction. A one-way clutch is installed in the one-way power transmission system. One end of the one-way power transmission system is connected to the drum (116), and the other end is connected to the hydraulic variable pump (113). When the elevator car descends, the drum (116) drives the hydraulic variable pump (113) through the one-way power transmission system. The hydraulic accumulator is connected to the hydraulic drive device and the hydraulic variable pump (113) through a high-pressure oil pipe. Each wire rope (200) corresponds to a drum (116), with one end connected to the drum (116) and the other end connected to the elevator car (300).

2. The hydraulic energy storage forced drive elevator according to claim 1, characterized in that, The traveling system includes a traveling system chassis (101), on which a linear guide rail (102) is placed and a traveling nut (101-1) is provided. A traveling vehicle (103) is placed on the linear guide rail (102). A traveling screw sprocket (105) is fixed on a traveling screw (104). The traveling screw (104) is screwed onto the traveling nut (101-1) and installed on the traveling vehicle (103). The traveling screw sprocket (105) is connected to the traveling vehicle drive sprocket (106) via a chain. A first bracket (122) is fixed on the traveling vehicle (103). It also includes a brake motor (111) for driving a hydraulic variable pump (113).

3. The hydraulic energy storage forced drive elevator according to claim 1, characterized in that, Several rolls (116) are connected in series and / or in parallel; When several drums (116) are connected in series, the hydraulic drive device includes: The hydraulic variable motor (109), clutch-type planetary gear (108), first gear (107) and fourth gear (115) are connected to the output shaft of the hydraulic variable motor (109). The clutch-type planetary gear (108) is connected to the first gear (107). The first gear (107) and the fourth gear (115) mesh. Several drums (116) and the fourth gear (115) are fixed on the first drive shaft (118). The first drive shaft (118) is rotatably mounted on the first bracket (122). When several drums (116) are connected in parallel, or in series and in parallel, the hydraulic drive device includes: The system includes a hydraulic variable displacement motor (109), a clutch-type planetary gear (108), a first gear (107), a third gear (114), and a fourth gear (115). The output shaft of the hydraulic variable displacement motor (109) is connected to the clutch-type planetary gear (108), which is connected to the first gear (107). The first gear (107) meshes with both the third gear (114) and the fourth gear (115). At least one drum (116) and the fourth gear (115) are fixed on a first drive shaft (118), which is rotatably mounted on a first bracket (122). The remaining drums (116) and the third gear (114) are fixed on a second drive shaft (119), which is rotatably mounted on the first bracket (122).

4. A hydraulic energy storage forced drive elevator according to claim 3, characterized in that, The clutch-type planetary gear (108) includes an input-side planetary gear set and an output-side planetary gear set; the gear ring (108-4) in the input-side planetary gear set is provided with a gear ring shaft, and a first one-way bearing (108-7) is sleeved on the gear ring shaft; the outer ring of the first one-way bearing (108-7) is fixed, and the inner ring is fixed on the gear ring shaft of the gear ring (108-4); The first sun gear shaft (108-1) in the input-side planetary gear set is connected to the output shaft of the hydraulic variable motor (109), and the second planet carrier (108-6) in the output-side planetary gear set is connected to the third drive shaft (120). The drive sprocket (106) and the first gear (107) are mounted on the third drive shaft (120) and rotate with the third drive shaft (120).

5. A hydraulic energy storage forced drive elevator according to claim 3, characterized in that, The unidirectional power transmission system includes a rotational speed coupling planetary gear (110) and a second gear (112). The rotational speed coupling planetary gear (110) includes an input-side planetary gear set and an output-side planetary gear set; the third sun gear shaft (110-1) of the input-side planetary gear set and the planet carrier (110-3) of the output-side planetary gear set are connected by a first one-way clutch (110-2), the outer ring of the first one-way clutch (110-2) is fixed to the third sun gear shaft (110-1) of the input-side planetary gear set, and the inner ring is fixed to the planet carrier (110-3) of the output-side planetary gear set; a second one-way bearing (110-7) is installed on the planet carrier (110-3) of the output-side planetary gear set. The third drive shaft (120) is connected to the planet carrier of the input planetary gear set, and the sun gear of the output planetary gear set is connected to the output shaft of the brake motor (111). The sun gear shaft of the output planetary gear set or the output shaft of the brake motor (111) is equipped with a third one-way bearing. The fourth gear ring (110-6) of the output planetary gear set is provided with external teeth, which mesh with the second gear (112). The second gear (112) is connected to the input shaft of the hydraulic variable pump (113).

6. A hydraulic energy storage forced drive elevator according to claim 4 or 5, characterized in that, The input-side planetary gear and output-side planetary gear in the clutch-type planetary gear (108), and the input-side planetary gear and output-side planetary gear in the speed-coupled planetary gear (110) are single-stage or multi-stage planetary gears.

7. A hydraulic energy storage forced drive elevator according to claim 1, characterized in that, It also includes a wire rope tension equalizer (400), with one wire rope tension equalizer (400) corresponding to each wire rope (200); The wire rope tension equalizer (400) includes a cylinder (401), inside which a metal bellows disc (403) is fixed, forming a sealed cavity filled with a shear-thickening fluid (402) or hydraulic oil. The cylinder (401) is provided with a connecting port and an exhaust port, which are connected to the cavity. The connecting ports of several wire rope tension equalizers (400) are connected in series through hydraulic connecting pipes and hydraulic damping holes. An inner cylinder liner (408) is fitted into the cylinder (401), and a piston (406) is fitted into the inner cylinder liner (408). The metal bellows disc (403), the inner cylinder liner (408), and the piston... The cavity formed between (406) is filled with single-sized micro steel balls (405); a ball seat (406-1) is provided at the bottom of the piston (406), and a protrusion (410-1) is provided on the lever shaft (410), which abuts against the ball seat (406-1); a through hole is provided at one end of the lever shaft (410), which is rotatably fitted on the fixed support (409), and a steel wire rope (200) is fixed at the other end; the cylinder (401) is fixed on the second bracket (412), and the second bracket (412) and the fixed support (409) are both fixed on the elevator car (300).

8. A hydraulic energy storage forced drive elevator according to claim 7, characterized in that, The other end of the lever shaft (410) is also provided with a through hole for installing a coarse adjustment bolt (411); the upper part of the coarse adjustment bolt (411) is connected to a wire rope (200), and the lower part is screwed into a nut.

9. A hydraulic energy storage forced drive elevator according to claim 7, characterized in that, The surface of the metal corrugated disc (403) is covered with a liner (404); the surface of the piston (406) is covered with a bushing (407).

10. A hydraulic energy storage forced drive elevator according to claim 3, characterized in that, It also includes at least one normally closed brake device (117), which is mounted on the first drive shaft (118) and / or the second drive shaft (119).

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