EP3073133B1 - Output shaft of cycloid hydraulic motor and shaft valve flow-distribution cycloid hydraulic motor - Google Patents

Output shaft of cycloid hydraulic motor and shaft valve flow-distribution cycloid hydraulic motor Download PDF

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Publication number
EP3073133B1
EP3073133B1 EP14863301.9A EP14863301A EP3073133B1 EP 3073133 B1 EP3073133 B1 EP 3073133B1 EP 14863301 A EP14863301 A EP 14863301A EP 3073133 B1 EP3073133 B1 EP 3073133B1
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EP
European Patent Office
Prior art keywords
output shaft
hydraulic motor
casing
cycloid hydraulic
needle bearing
Prior art date
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EP14863301.9A
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German (de)
French (fr)
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EP3073133A1 (en
EP3073133A4 (en
EP3073133B8 (en
Inventor
Zhisheng Wang
Zhimin Zhang
Changqing Zhang
Yuchuan SHENG
Feng Zhou
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Zhenjiang dali hydraulic motor co Ltd
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Zhenjiang dali hydraulic motor co Ltd
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Priority to CN201310584115.5A priority Critical patent/CN103629042B/en
Priority to CN201310584259.0A priority patent/CN103671465B/en
Application filed by Zhenjiang dali hydraulic motor co Ltd filed Critical Zhenjiang dali hydraulic motor co Ltd
Priority to PCT/CN2014/083430 priority patent/WO2015074440A1/en
Publication of EP3073133A1 publication Critical patent/EP3073133A1/en
Publication of EP3073133A4 publication Critical patent/EP3073133A4/en
Publication of EP3073133B1 publication Critical patent/EP3073133B1/en
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Publication of EP3073133B8 publication Critical patent/EP3073133B8/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03CPOSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00Rotary-piston engines
    • F03C2/08Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00Rotary-piston machines or engines
    • F01C1/08Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/104Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F01C1/105Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement and having an articulated driving shaft
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02Arrangements of bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/105Details concerning timing or distribution valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/50Bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/60Shafts

Description

    CROSS REFERENCE TO RELATED APPLICATIONS
  • The present application claims the benefit of the priority of Chinese Patent Application No. 201310584115.5, filed on November 20, 2013 , entitled "Axle Valve Flow-distribution Cycloid Hydraulic Motor", and the priority of Chinese Patent Application No. 201310584259.0, filed on January 17, 2014 , entitled "Output Shaft of Cycloid Hydraulic Motor and Processing Method thereof".
  • TECHNICAL FIELD
  • The present disclosure relates to an axle valve flow-distribution cycloid hydraulic motor having the output shaft of the cycloid hydraulic motor, belonging to the technical field of hydraulic transmission.
  • BACKGROUND
  • A cycloid hydraulic motor is a motor with a low speed and a high torque, having advantages of small size, large unit power density, high efficiency, wide range of rotating speed and so on, and is widely used. Especially, the axle-flow-distribution cycloid hydraulic motor is suitable for the applications that need lower pressure levels and higher cost performances, as it has a simple structure and low cost. In order to ensure the lubrication of the axle-flow-distribution valve, and to form the desired flow-distribution oil film and the reliable seal, circumferential annular oil grooves are disposed on the output shaft, but the configuration of such oil grooves is unfavorable for the radial bearing capacity of the output shaft.
  • The basic configuration of the cycloid hydraulic motor includes a liquid feed port and a return port disposed on the casing or the rear cover; the cycloid hydraulic motor has a cycloidal gear pair and a flow-distribution mechanism installed at one end, wherein the flow-distribution mechanism may be placed ahead of or behind the cycloidal gear pair, typically it adopts the axle valve flow-distribution when it is placed in the front, and it adopts the plane flow-distribution when it is placed in the rear, and the cycloid hydraulic motor has an output shaft at the other end. The rotor of the cycloidal gear pair is engaged with an external gear installed on one end of a linkage shaft through internal keys, and the other end of the linkage shaft is transmissibly connected with the output shaft.
  • When in operation, by means of the flow-distribution mechanism, the liquid feed port is communicated with an extended engaging cavity of the cycloidal gear pair, and the shrunk engaging cavity of the cycloidal gear pair is communicated with the return port. As a result, pressurized liquid enters the casing or the rear cover through the liquid feed port, then enters the extended engaging cavity formed by the cycloidal gear pair, causing the volume of the extended engaging cavity expanded gradually, at the same time, the liquid in the shrunk engaging cavity formed by the cycloidal gear pair returns through the return port. In this process, the rotor of the cycloidal gear pair is driven to rotate by the pressure difference between the extended engaging cavity and the shrunk engaging cavity, and the rotation is transmitted to the output shaft through the linkage shaft and is output from the output shaft, thereby the hydraulic energy is converted into the mechanical energy. Meanwhile, the flow-distribution mechanism (also called as the axle valve) is also driven to rotate by the linkage shaft, and is switched between a closed state and an opened state again and again, so that the converting process is continued, and the motor outputs the torque continuously.
  • As far as the applicant knows, the prior art compact axle valve flow-distribution cycloid hydraulic motor is developed rapidly (such as the products BM1, BMP and BMR manufactured by the applicant). Although the sliding bearing of the flow-distribution mechanism of the prior art hydraulic motor can bear a certain radical force, as limited by its structure, it is not suitable for driving an external engaging gear or chain gear or directly driving other components having larger radical force, even if a radial needle bearing or a ball bearing is added (e.g., Chinese patent No. 200720041824.9 disclosed that radical needle bearings with different size are installed at the front and the rear as supporting elements, and Chinese patent No. 201220454428.X disclosed that a ball bearing is installed at the front end of the output shaft for bearing radical force), the capacity of bearing large radical force still cannot be improved remarkably, whereas the leakage may be increased.
  • DE 10 2007 017 652 discloses providing support means in the region of recesses of a rotary slide arrangement in a motor shaft, to prevent increased leakage losses due to deformations in the motor shaft of a gerotor motor.
  • SUMMARY
  • The major objectives of the present disclosure are as follows: in view of the above-mentioned existing problem in the prior art, by modifying the configuration, to provide a method for processing the output shaft of the cycloid hydraulic motor.
  • Therefore, the steps of processing the intermittent oil grooves are as follows:
    • Step 1, clamping the primarily processed output shaft in a rotational turning or grinding fixture with its axis deviating from the rotating center of the turning or grinding fixture by the amount of the process eccentricity e;
    • Step 2, driving the turning or grinding fixture to rotate;
    • Step 3, when the turning tool or the grinding wheel contacts with the main body, processing according to the maximum height of the oil groove until a first intermittent oil groove is processed;
    • Step 4, on the premise of retaining the process eccentricity unchanged, turning the main body to the angular position of the adjacent intermittent oil groove, then clamping the output shaft at this position, and processing for the subsequent intermittent oil groove in the same way as described in the above Step 2 and Step 3.
  • By adopting the configuration of the output shaft of the cycloid hydraulic motor, the present disclosure prevents the output shaft from being disconnected by the annular oil groove, thus it is beneficial for enhancing the radial bearing capacity. And by means of common fixtures such as a four-jaw chuck (or a special tool), the desired oil groove can be processed directly, and there is no need to adopt the complicated milling process as required for processing the equi-depth circumferential intermittent oil grooves, therefore, it is beneficial for improving the efficiency remarkably, and reducing the manufacturing cost. Additionally, the present disclosure replaces the prior art equi-depth oil groove having the concentric arc bottom with the oil groove having the eccentric arc bottom and having a varying height decreasing gradually from the center to both ends, which is beneficial theoretically and practically for enabling oil contained in the oil groove flowing from both ends of the oil groove to the excircle area of the dynamic engaging portion of the main body between adjacent oil grooves, and then further diffusing to both sides, so that better oil film can be formed to ensure the lubrication and seal. With regard to the oil groove to be processed after the heat treatment, tooling equipment similar to a four-jaw chuck is adopted to grind the oil groove on a grinder.
  • A further objective of the present disclosure is to provide an axle valve flow-distribution cycloid hydraulic motor by modifying the configuration, which remains compact in structure, has an improved radial bearing capacity, an enhanced sealing effect, and has a good processability.
  • In order to achieve the above further objective, the present disclosure provides an axle valve flow-distribution cycloid hydraulic motor, comprising: a front cover and a casing, which are fixedly connected with each other, and a cycloidal gear pair formed by a stator and a rotor; the cycloidal gear pair is fixedly connected to a casing through a diaphragm at one end, and fixedly connected with a rear cover at the other end; an output shaft is arranged in the casing, an outer end of the output shaft extends out of the casing, the output shaft is transmissibly connected to the rotor through an linkage shaft; wherein, an inner hole of the casing is a through-hole with same inner diameter; a front needle bearing is installed on a front portion of the output shaft and a rear needle bearing is installed on a rear end of the output shaft; the front needle bearing has a same outer diameter but a greater length as compared with the rear needle bearing; a shoulder of the output shaft corresponding to a front end of the front needle bearing is abutted against a rear retaining ring of a plane thrust bearing; a dynamic engaging portion is disposed behind the front needle bearing on the output shaft for dynamically engaging with the casing, the dynamic engaging portion includes at least two circumferential intermittent oil grooves; a groove bottom of each intermittent oil groove is formed by an eccentric arc about a center point that deviates from a center point of an excircle of the dynamic engaging portion by a process eccentricity e, a radius of the eccentric arc is greater than a radius of the excircle of the dynamic engaging portion.
  • Further, a front retaining ring of the plane thrust bearing is installed against an end face of an stepped hole in the front cover, a shaft seal is arranged in the stepped hole and ahead of the front retaining ring.
  • Further, the output shaft includes a larger-diameter section assembled in the casing, and a smaller-diameter section extending out of the casing; the larger-diameter section has a front necked-down portion for installing the front needle bearing on an external circular surface at one end, and has a rear necked-down portion for installing the rear needle bearing on the external circular surface at the other end; a dynamic engaging portion for dynamically engaging with the inner hole of the casing is disposed between the front necked-down portion and the rear necked-down portion, and is closer to the front necked-down portion; three intermittent oil grooves distributed uniformly in a circumferential direction are disposed on the dynamic engaging portion.
  • Further, the shaft seal includes a metallic frame having an L-shaped cross-section, a polytetrafluoroethylene retaining ring having a rectangular cross-section, which is tightly adhered to an inner end face of the metallic frame and is sealedly engaged with the external surface of the output shaft, and a rubber seal lip that half surrounds the metallic frame and the polytetrafluoroethylene retaining ring.
  • Further, the rubber seal lip includes one seal engaging surface fit with the inner surface of the stepped hole in the front cover and another seal engaging surface fit with the external surface of the output shaft.
  • Further, the rubber seal lip is filled between the external surface of the polytetrafluoroethylene retaining ring and the metallic frame.
  • According to the axle valve flow-distribution cycloid hydraulic motor of the present disclosure, since the inner diameter of the casing is constant, it is very convenient for processing and assembling; as the bearings are arranged reasonably in consideration of the larger load on the front section, and the organic combination of the front needle bearing and the plane thrust bearing, the bearing capacity of the front needle bearing can be further improved. Therefore, as compared with the prior art, on the premise that the structure remains compact, the radial bearing capacity of the cycloid hydraulic motor is improved, and the axial bearing capacity is improved at the same time, and the cycloid hydraulic motor allows for convenient processing and has good assembling processability.
  • The dynamic engaging portion for dynamically engaging with the inner hole of the casing is located behind the front needle bearing installed on the output shaft, the dynamic engaging portion includes at least two circumferential intermittent oil grooves; the bottom of said intermittent oil groove is formed by an eccentric arc about a center point that deviates from a center point of an excircle of the dynamic engaging portion by a process eccentricity e, a radius of the eccentric arc is greater than a radius of the excircle of the dynamic engaging portion. Therefore, the present disclosure prevents the output shaft from being disconnected by the annular oil groove, thus it is beneficial for enhancing the radial bearing capacity. And by means of common fixtures such as a four-jaw chuck (or a special tool), the desired oil groove can be processed directly, and there is no need to adopt the complicated milling process as required for processing the equi-depth circumferential intermittent oil grooves, therefore, it is beneficial for improving the efficiency remarkably, and reducing the manufacturing cost. Additionally, the present disclosure replaces the prior art equi-depth oil groove having the concentric arc bottom with the oil groove having the eccentric arc bottom and having a varying height decreasing gradually from the center to both ends, which is beneficial theoretically and practically for enabling oil contained in the oil groove flowing from both ends of the oil groove to the excircle area of the dynamic engaging portion of the main body between adjacent oil grooves, and then further diffusing to both sides, so that better oil film can be formed to ensure the lubrication and seal.
  • In the present disclosure, the front retaining ring of the plane thrust bearing is installed against the end face of the stepped hole in the front cover, a shaft seal is arranged in the stepped hole and ahead of the front retaining ring, so as to ensure the reliably sealing effect.
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • The present disclosure will be described in more details with reference to the accompanying figures.
    • Fig. 1 is a schematic structural diagram illustrating the embodiment 1 of the present invention;
      Wherein the elements are denoted as follows: output shaft 1, key 2, dust seal 3, shaft seal 4, screw 5, front cover 6, valve body 7, seal ring 8, valve ball 9, casing 10, oil port cap 11, O-ring 12, diaphragm 13, cycloidal gear pair 14, rear cover 15, plug 16, gasket 17, steel gasket 18, bolt 19, rear needle bearing 20, linkage shaft 21, front needle bearing 22, rear retaining ring 23, O-ring 24, plane thrust bearing 25, front retaining ring 26;
    • Fig. 2 is a schematic structural diagram illustrating the output shaft in the embodiment of Fig. 1;
    • Fig. 3 is a cross-section view of a rotor-stator pair in the embodiment of Fig. 1;
    • Fig. 4 is an illustrative geometric relationship diagram of the relevant parameters in a cross-section of the intermittent oil grooves taken along the direction of the arrows at the dynamic engaging portion shown in Fig. 2;
    • Fig. 5 is an enlarged view of the shaft seal in the embodiment of Fig. 1;
    • Fig. 6 is a schematic structural diagram illustrating the embodiment 2 of the present invention;
    • Fig. 7 is a cross-section view of a rotor-stator pair in the embodiment of Fig. 6.
    DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1:
  • Figs. 1 and 3 illustrate the basic configuration of the axle valve flow-distribution cycloid hydraulic motor of this embodiment. Similar as the prior art, the present disclosure comprises a front cover 6 and a casing 10, which are fixedly connected with each other, and a cycloidal gear pair formed by a stator and a rotor; the cycloidal gear pair is fixedly connected to the casing 10 through a diaphragm 13 at one end, and fixedly connected with a rear cover 15 at the other end. An output shaft 1 is arranged in the casing 10, the outer end of the output shaft extends out of the casing, the internal key of the output shaft is transmissibly connected to the internal key of the rotor through a linkage shaft 21.
  • The inner hole of the casing 10 is a through-hole with the same inner diameter. A front needle bearing 22 is installed on the front portion of the output shaft 1 and a rear needle bearing 20 is installed on the rear end of the output shaft 1; the front needle bearing 22 has the same outer diameter but a greater length as compared with the rear needle bearing 20. The shoulder of the output shaft 1 corresponding to the front end of the front needle bearing 22 is abutted against the rear retaining ring 23 of the plane thrust bearing 25.
  • As shown in Fig. 2, the output shaft 1 includes a larger-diameter section 1-2 assembled inside the casing 10 of the cycloid hydraulic motor, and a smaller-diameter section 1-1 extending out of the casing. A key groove is disposed on the smaller-diameter section 1-1, so that power and motion can be transmitted through the key-connection. An internal key engaging structure transmissibly connected with the linkage shaft 21 of the cycloid hydraulic motor is disposed in the inner hole of the larger-diameter section 1-2; the larger-diameter section has a front necked-down portion for installing the front needle bearing 22 on the external circular surface at one end, and has a rear necked-down portion for installing the rear needle bearing 20 on the external circular surface at the other end; a dynamic engaging portion 1-2-1 for dynamically engaging with the inner hole of the casing 10 is disposed between the front necked-down portion and the rear necked-down portion, and is closer to the front necked-down portion; additionally, other components are provided between the front necked-down portion and rear necked-down portion for forming the axle-flow-distribution, these components are the same as those of the prior art, and are not described here for brevity. Three intermittent oil grooves 1-2-2 distributed uniformly in the circumferential direction are disposed on the dynamic engaging portion 1-2-1. As shown in Fig. 4, the groove bottom of each intermittent oil groove 1-2-2 is formed by an eccentric arc about the center O', said center O' is deviated from the center O of the excircle of the dynamic engaging portion by a process eccentricity e, the radius R of the eccentric arc is greater than the radius r of the excircle of the dynamic engaging portion 1-2-1. It is evident that, e=R+h-r; wherein, e is the process eccentricity (mm); R is the radius of the eccentric arc; h is the maximum height of the intermittent oil groove, which is generally between 0.3mm to 1.0mm; r is the radius of the dynamic engaging portion. The radii of the flow-distribution axles of different series of hydraulic motors are different, for example, the radii of BMP and BMR series are ranged from 21 mm to 21.5 mm. When it is designed, the radius r of the dynamic engaging portion, the length 1 of the outer arc of the intermittent oil groove (or its corresponding central angle A, which is generally between 30° and 65°), and the maximum height h are identical to those of the prior art circumferentially-spaced oil grooves with the concentric arc bottom and the same height. According to common mathematic knowledge, such as cosine law and so on, and with reference to Fig. 3, it is not difficult to find the geometric relationship between these parameters, then obtain simultaneous equations to solve for the process eccentricity e and the radius R of the eccentric arc.
  • The front retaining ring 26 of the plane thrust bearing 25 is installed against the end face of the stepped hole in the front cover 6, a shaft seal 4 is arranged in the stepped hole and ahead of the front retaining ring 26. The specific structure of the shaft seal is shown in Fig. 5, which includes a metallic frame 4-1 having an L-shaped cross-section, a polytetrafluoroethylene retaining ring 4-2 having a rectangular cross-section, which is tightly adhered to the inner end face of the metallic frame 4-1 and is sealedly engaged with the external surface of the output shaft 1, and a rubber seal lip 4-3 that half surrounds the metallic frame 4-1 and the polytetrafluoroethylene retaining ring 4-2. Said rubber seal lip 4-3 includes one seal engaging surface fit with the inner surface of stepped hole in the front cover 6 and another seal engaging surface fit with the external surface of the output shaft. The rubber seal lip 4-3 is filled between the external surface of the polytetrafluoroethylene retaining ring 4-2 and the metallic frame 4-1.
  • In addition, an oil return circulation channel communicated with the inner cavity is disposed in the casing 10, and two unidirectional valves are arranged in the oil return circulation channel, each unidirectional valve includes a valve body 7, a seal ring 8 and a valve ball 9. One end of one unidirectional valve is connected with the oil feed port and one end of another unidirectional valve is connected with the oil return port, the other ends of the two unidirectional valves are communicated with the inner cavity of the motor via the inner unidirectional valve oil return channel between the front cover 6 and the casing 10. Such arrangement helps to protect the shaft seal.
  • In processing, since the inner hole of the casing 10 is a straight-hole with the same diameter, only one pass is needed for processes such as lathing, grinding, and so on; it is very convenient for processing, and the dimensional accuracy and geometrical accuracy can be ensured. The steps of processing the intermittent oil grooves on the output shaft are as follows: Step 1, clamping the primarily processed output shaft in an index chuck, specifically, the output shaft is clamped in a four-jaw chuck of a lathe with its axis deviating from the rotating center of the turning fixture of the lathe by the amount of the process eccentricity e; Step 2, starting the lathe, driving the four-jaw chuck to rotate; Step 3, employing a lathe tool with a cutting tip conforming to the shape of the cross-section of the intermittent oil groove; when the cutting tip contacts with the output shaft, feeding the lathe tool according to the maximum height of the oil groove, then a first intermittent oil groove is processed; Step 4, on the premise of retaining the process eccentricity unchanged, successively turning the output shaft by 120° and 240° relative to the angular position of the four-jaw chuck, clamping the output shaft at each position, and processing for the second intermittent oil groove and the third intermittent oil groove in the same way as described in the above Step 2 and Step 3.
  • Embodiment 2:
  • As shown in Figs. 6 and 7, the basic configuration of the axle valve flow-distribution cycloid hydraulic motor of this embodiment is similar to that of the embodiment 1. The embodiment 2 is different from the embodiment 1 mainly in that, the cycloidal gear pair in the embodiment 2 is an embedded column type rotor-stator pair, while the cycloidal gear pair in the embodiment 1 is an integrated rotor-stator pair.
  • Experiments have proved that, since a series of modifications seemingly tiny but effective were made in the above-mentioned embodiments, the radial bearing capacity of the hydraulic motor has been improved by nearly 40%, meanwhile the axial bearing capacity has been improved. The hydraulic motor has compact structure, smaller size, better machining and assembling processes, thereby the cost performance is further improved as compared with the traditional products.

Claims (6)

  1. An axle valve flow-distribution cycloid hydraulic motor, comprising: a front cover (6) and a casing (10), which are fixedly connected with each other, and a cycloidal gear pair (14) formed by a stator and a rotor; wherein, the cycloidal gear pair (14) is fixedly connected to a casing (10) through a diaphragm (13) at one end, and fixedly connected with a rear cover (15) at the other end; an output shaft (1) is arranged in the casing (10), an outer end of the output shaft (1) extends out of the casing (10), the output shaft (1) is transmissibly connected to the rotor through a linkage shaft (21); an inner hole of the casing (10) is a through-hole with same inner diameter; a front needle bearing (22) is installed on a front portion of the output shaft (1) and a rear needle bearing (20) is installed on a rear end of the output shaft (1); the front needle bearing (22) has a same outer diameter but a greater length as compared with the rear needle bearing (20); a shoulder of the output shaft (1) corresponding to a front end of the front needle bearing (22) is abutted against a rear retaining ring (23) of a plane thrust bearing (25); characterized in that it further comprises a dynamic engaging portion (1-2-1) disposed behind the front needle bearing (22) on the output shaft (1) for dynamically engaging with the casing (10), the dynamic engaging portion (1-2-1) includes at least two circumferential intermittent oil grooves (1-2-2); a groove bottom of each intermittent oil groove (1-2-2) is formed by an eccentric arc about a center point (O') that deviates from a center point (O) of an excircle of the dynamic engaging portion by a process eccentricity e, a radius (R) of the eccentric arc is greater than a radius (r) of the excircle of the dynamic engaging portion (1-2-1).
  2. The axle valve flow-distribution cycloid hydraulic motor according to claim 1, wherein, a front retaining ring (26) of the plane thrust bearing (25) is installed against an end face of an stepped hole in the front cover (6), a shaft seal (4) is arranged in the stepped hole and ahead of the front retaining ring (26).
  3. The axle valve flow-distribution cycloid hydraulic motor according to claim 2, wherein, the output shaft (1) includes a larger-diameter section (1-2) assembled inside the casing (10), and a smaller-diameter section (1-1) extending out of the casing (10); the larger-diameter section (1-2) has a front necked-down portion for installing the front needle bearing (22) on an external circular surface at one end, and has a rear necked-down portion for installing the rear needle bearing (20) on the external circular surface at the other end; a dynamic engaging portion (1-2-1) for dynamically engaging with the inner hole of the casing (10) is disposed between the front necked-down portion and the rear necked-down portion, and is closer to the front necked-down portion; three intermittent oil grooves (1-2-2) distributed uniformly in a circumferential direction are disposed on the dynamic engaging portion (1-2-1).
  4. The axle valve flow-distribution cycloid hydraulic motor according to claim 3, wherein, the shaft seal (4) includes a metallic frame (4-1) having an L-shaped cross-section, a polytetrafluoroethylene retaining ring (4-2) having a rectangular cross-section, which is tightly adhered to an inner end face of the metallic frame (4-1) and is sealedly engaged with the external surface of the output shaft (1), and a rubber seal lip (4-3) that half surrounds the metallic frame (4-1) and the polytetrafluoroethylene retaining ring (4-2).
  5. The axle valve flow-distribution cycloid hydraulic motor according to claim 4, wherein, the rubber seal lip (4-3) includes one seal engaging surface fit with the inner surface of the stepped hole in the front cover (6) and another seal engaging surface fit with the external surface of the output shaft (1).
  6. The axle valve flow-distribution cycloid hydraulic motor according to claim 5, wherein, the rubber seal lip (4-3) is filled between the external surface of the polytetrafluoroethylene retaining ring (4-2) and the metallic frame (4-1).
EP14863301.9A 2013-11-20 2014-07-31 Output shaft of cycloid hydraulic motor and shaft valve flow-distribution cycloid hydraulic motor Active EP3073133B8 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201310584115.5A CN103629042B (en) 2013-11-20 2013-11-20 Axle valve flow distribution cycloid hydraulic motor
CN201310584259.0A CN103671465B (en) 2014-01-17 2014-01-17 A kind of cycloid hydraulic motor output shaft and processing method thereof
PCT/CN2014/083430 WO2015074440A1 (en) 2013-11-20 2014-07-31 Output shaft of cycloid hydraulic motor and shaft valve flow-distribution cycloid hydraulic motor

Publications (4)

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EP3073133A1 EP3073133A1 (en) 2016-09-28
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US10920758B2 (en) 2018-06-29 2021-02-16 Bendix Commercial Vehicle Systems Llc Hypocycloid compressor

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EP3073133B8 (en) 2019-06-05
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EP3073133A1 (en) 2016-09-28

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