EP2570590B1 - Mehrstufiger pneumatikmotor - Google Patents

Mehrstufiger pneumatikmotor Download PDF

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Publication number
EP2570590B1
EP2570590B1 EP10851297.1A EP10851297A EP2570590B1 EP 2570590 B1 EP2570590 B1 EP 2570590B1 EP 10851297 A EP10851297 A EP 10851297A EP 2570590 B1 EP2570590 B1 EP 2570590B1
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EP
European Patent Office
Prior art keywords
stage
motor
gear
pneumatic motor
power output
Prior art date
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Not-in-force
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EP10851297.1A
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English (en)
French (fr)
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EP2570590A4 (de
EP2570590A1 (de
Inventor
Chunbao Feng
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Jikai (hebei) Mechatronics Technology Co Ltd
Original Assignee
Jikai (hebei) Mechatronics Technology Co Ltd
Jikai Hebei Mechatronics Tech Co Ltd
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Publication of EP2570590A4 publication Critical patent/EP2570590A4/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/18—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/02—Control of, monitoring of, or safety arrangements for, machines or engines specially adapted for several machines or engines connected in series or in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing type

Definitions

  • the present invention relates to a pneumatic motor which belongs to the field of mechanical engineering and is used on sites of industrial and mining operation, and particularly relates to an energy-saving and efficient multistage pneumatic motor.
  • a pneumatic motor is a mechanical device which takes compressed air as a power source, and has been widely used due to advantages of being light and safe and etc., and is especially widely used on operation sites where electricity is not allowed as a power source and is also a must.
  • Currently used pneumatic motors are all single stage motors. Wherein, the pneumatic motors have many forms of structures, comprising a gear-type motor, a plunger-type motor, a vane-type motor, a screw-type motor and etc., and the most widely used motor in industry such as coal mining is the gear-type motor.
  • the single stage gear-type pneumatic motor is to provide a pair of gears engaging with each other within a shell, in which the gear shaft of one gear is a power output shaft connected with devices such as a reducer and outputs power.
  • the shell of the gear-type pneumatic motor is respectively provided with an inlet and an outlet for the compressed air, and when passing the gear-type pneumatic motor, the compressed air pushes the gears of the motor to rotate, thereby forming power output.
  • GB 999 459 A as well as WO 2009/034421 A1 disclose a multistage numatic motor as per the preamble of claim 1.
  • the multistage numatic motor as per the invention comprises the features of the characterizing portion of claim 1.
  • a multistage pneumatic motor provided by the present invention comprises a shell and a power output main shaft, and the shell is provided with a gas inlet and a gas outlet, characterized in that, two or more pneumatic motor stages are installed in the shell, the first pneumatic motor stage among the two or more pneumatic motor stages is communicated with the gas inlet, and the last pneumatic motor stage is communicated with the gas outlet, a power gas enters the shell through the gas inlet, drives the first pneumatic motor stage and then the second pneumatic motor stage, then drives the next pneumatic motor stage, and is exhausted from the shell through the gas outlet at last, every pneumatic motor stage is provided with a power output shaft which is connected to the power output main shaft, so that the powers produced by all the pneumatic motor stages are jointed together and then output by the power output main shaft.
  • the rotating speeds delivered by the power output shafts of each stage of the pneumatic motor to the power output main shaft are the same, so that the powers produced by each stage of the pneumatic motor are joined forwardly and then outputted by the power output main shaft.
  • the pneumatic motor is a gear motor, a vane motor, a plunger motor or a screw motor.
  • the shell is provided therein with a first pneumatic motor stage consisting of a pair of a first-stage motor gear and a second pneumatic motor stage consisting of a pair of a second-stage motor gear
  • one gear shaft of the first-stage motor gears is the power output shaft of the first pneumatic motor stage
  • one gear shaft of the second-stage motor gears is the power output shaft of the second pneumatic motor stage
  • the power output shaft of the first pneumatic motor stage, the power output shaft of the second pneumatic motor stage and the power output main shaft are the same shaft
  • the first-stage motor gear and the second-stage motor gear have the same number of teeth and the same modulus
  • the first-stage motor gear is shorter than that of the second-stage motor gear, so that the rotating speed of the power output shaft of the first pneumatic motor stage is the same with the rotating speed of the power output shaft of the second pneumatic motor stage.
  • the shell is provided therein with a first pneumatic motor stage consisting of a pair of a first-stage motor gear, a second pneumatic motor stage consisting of a pair of a second-stage motor gear and a third pneumatic motor stage consisting of a pair of a third-stage motor gear, and the power output shafts of the first pneumatic motor stage, the second pneumatic motor stage and the third pneumatic motor stage are connected with the power output main shaft through a transmission gear.
  • the first pneumatic motor stage, the second pneumatic motor stage and the third pneumatic motor stage surround the power output main shaft and are arranged in a circular shape
  • the power output main shaft is located at the centre of the respective pneumatic motor stages
  • one gear shaft of each pair of motor gear stages is the power output shaft of each pneumatic motor stage
  • the transmission gear comprises a driving gear provided on the power output shaft of each pneumatic motor stage and a driven gear provided on the power output main shaft while engaging with the driving gear of each pneumatic motor stage.
  • the driving gear provided on the power output shaft of each pneumatic motor stage is a gear formed on the power output shaft, so that the power output shaft of each pneumatic motor stage becomes a driving gear shaft, and the driving gears on the driving gear shafts of respective pneumatic motor stages have the same the modulus and the same number of teeth.
  • the first pneumatic motor stage, the second pneumatic motor stage and the third pneumatic motor stage are arranged in a linear shape, one gear shaft of each pair of motor gear stages is the power output shaft of each pneumatic motor stage, the transmission gear comprises three first-stage driving gears provided on the power output shaft of each pneumatic motor stage, two first-stage driven gears simultaneously engaging with the first-stage driving gears of the adjacent pneumatic motor stages, two second-stage driving gear shafts being respectively coaxial with the two first-stage driven gears, and one second-stage driven gear simultaneously engaging with the two second-stage driving gear shafts, and the one second-stage driven gear shaft is provided on the power output main shaft.
  • the three first-stage driving gears have the same modulus and the same number of teeth
  • the two first-stage driven gears have the same modulus and the same number of teeth
  • the two second-stage driving gear shafts have the same modulus and the same number of teeth.
  • the first-stage motor gear, the second-stage motor gear and the third-stage motor gear have the same number of teeth and the same gear length, and the modulus of the gears increase stage by stage so that the rotating speeds of the power output shafts of the respective pneumatic motor stages are the same.
  • the first-stage motor gear, the second-stage motor gear and the third-stage motor gear have the same number of teeth and the same modulus, and the lengths of the gears increase stage by stage so that the rotating speeds of the power output shafts of the respective pneumatic motor stages are the same.
  • the first-stage motor gear, the second-stage motor gear and the third-stage motor gear have the same modulus and the same gear length, and the numbers of the teeth of the gears increase stage by stage so that the rotating speeds of the power output shafts of the respective pneumatic motor stages are the same.
  • the first pneumatic motor stage, the second pneumatic motor stage and the third pneumatic motor stage surround the power output main shaft and are arranged in a circular shape
  • the power output main shaft is located at the centre of the respective pneumatic motor stages
  • one gear shaft of each pair of motor gear stages is the power output shaft of each pneumatic motor stage
  • the transmission gear comprises respective transmission gears of the respective motor gear stages with different reduction ratios and a driven gear provided at the power output main shaft, and the rotating speeds delivered from the respective pneumatic motor stages to the power output main shaft are the same.
  • the multistage pneumatic motor provided according to the present invention, multiple pneumatic motor stages are provided within the shell, and the powers at the power output shafts of the multiple pneumatic motor stages are joined together and then output through a power output main shaft, that is, multiple pneumatic motors are connected in series and used jointly, then the gas energy of the compressed air is fully used, so that the gas energy discharged out of the pneumatic motor are lowered to the minimum extent, and the energy of the compressed air is fully used, thereby improving the working efficiency of the pneumatic motor and lowering the noise of the discharged gas.
  • the efficiency of the three-stage pneumatic gear motor provided by the present invention can be enhanced by 40%-50% compared with the current single-stage pneumatic gear motor, and the noise can be lowered by at least 10 decibels based on the prior art.
  • the working principle of the multistage pneumatic motor of the present invention is as follow: after the compressed air enters the shell of the multistage motor, the pressure of the gas lowers while its volume increases after passing each pneumatic motor stage, then, according to a gas state equation, without considering temperature changes, the pressure of the gas is in inverse proportion to the volume of the gas, that is, the volume of the gas will increase when the pressure of the gas lowers.
  • the present invention fully considers the changes of gas pressure and volume between multistage motor, and uses many methods to achieve that the rotating speeds delivered from the respective motor stages to the power output main shaft are substantially the same, so as to reduce the mutual interference between the respective motor stages and achieve the forward joining of the powers of the respective pneumatic motor stages, which greatly enhances the total output power.
  • Embodiment 1 illustrates the structure of a two-stage pneumatic gear motor of the present invention, and the two-stage pneumatic motor comprises a shell 1 and a power output main shaft 2, and the shell 1 is provided with a gas inlet 3 and a gas outlet 4, characterized in that, the shell 1 is provided therein with two pneumatic gear motor stages, i.e., a first pneumatic gear motor stage 11 consisting of a pair of a first-stage motor gear 111 and a second pneumatic gear motor stage 12 consisting of a pair of a second-stage motor gear 121, the first pneumatic gear motor stage 11 is communicated with the gas inlet 3, the last pneumatic gear motor stage, i.e., the second pneumatic gear motor stage 12, is communicated with the gas outlet 4, and a power gas enters the shell 1 through the gas inlet 3 and then drives the first pneumatic gear motor stage 11 and then the second pneumatic gear motor stage 12, and is finally discharged out of the shell 1 through the gas outlet 4, the first pneumatic gear motor stage 11 is
  • each pneumatic gear motor stage is provided with a power output shaft, and the power output shaft of each pneumatic gear motor stage is connected with the power output main shaft, so that the powers produced by each of the pneumatic gear motor stages are joined together and then output by the power output main shaft, thus the energy of the compressed gas is fully used, the efficiency of the pneumatic motor is improved, and the speed and the pressure of the fully used compressed gas discharged out of the shell are lowered greatly, and thus the noise of the pneumatic motor is decreased.
  • the rotating speeds delivered from the power output shafts of each stage of the pneumatic gear motor to the power output main shaft are the same, so that the powers produced by each stage of the pneumatic gear motor are joined forwardly and then outputted by the power output main shaft.
  • the power gas can be used to the most extent to improve the efficiency of the pneumatic motor to the greatest extent.
  • one gear shaft of the first-stage motor gears 111 is the power output shaft 112 of the first pneumatic gear motor stage 11
  • one gear shaft of the second-stage motor gears 121 is the power output shaft 122 of the second pneumatic gear motor stage 12
  • the power output shaft 122 of the second pneumatic gear motor stage 12 and the power output main shaft 2 are the same shaft
  • the first-stage motor gear 111 and the second-stage motor gear 121 have the same number of teeth and the same modulus
  • the first-stage motor gear 111 is shorter than the second-stage motor gear 121, so that the rotating speed of the power output shaft 112 of the first pneumatic gear motor stage 11 is the same with the rotating speed of the power output shaft 122 of the second pneumatic gear motor stage 12.
  • the relationship between the lengths of the first-stage motor gear 111 and the second-stage motor gear 121 it can be determined according to the inverse proportion relationship between the pressure and the volume of the compressed air and then in combination with the value of the compressed air which has passed the two pneumatic gear motor stages. This can be rendered via simple mathematic calculation, which can be conducted by those skilled in the art and thus is omitted herein.
  • the motor can be other forms of pneumatic motors, and although the above embodiment of the two-stage gear motor achieves, through the length relationship between the motor gears, the same rotating speed delivered from the first motor stage and the second motor stage to the power output main shaft, and then achieves the forward joining of the powers of the two motor stages, those skilled in the art would know achieving the same rotating speed delivered from the two gear motor stages to the power output main shaft through changing the modulus or the number of teeth of the motor gears, or through changing both the modulus and the number of teeth of the motor gears; in addition, a gear shift mechanism can be used to achieve the same rotating speed delivered from the two gear motor stages to the power output main shaft, and then to achieve the objects of the present invention.
  • Embodiment 2 illustrate the structure of a three-stage pneumatic gear motor according to the present invention, and the three-stage pneumatic gear motor comprises a shell 1 and a power output main shaft 2, and the shell 1 is provided with a gas inlet 3 and a gas outlet 4, characterized in that, the shell 1 is provided therein with three pneumatic gear motor stages, i.e., a first pneumatic gear motor stage 11 consisting of a pair of a first-stage motor gear 111, a second pneumatic gear motor stage 12 consisting of a pair of a second-stage motor gear 121 and a third pneumatic gear motor stage 13 consisting of a pair of a third-stage motor gear 131, the first pneumatic gear motor stage 11 is communicated with the gas inlet 3, the last pneumatic gear motor stage, i.e., the third pneumatic gear motor stage 13, is communicated with the gas outlet 4, and a power gas enters the shell 1 through the gas inlet 3 and then drives the first pneumatic gear motor stage 11 and then the second
  • the first pneumatic motor stage 11, the second pneumatic motor stage 12 and the third pneumatic motor stage 13 surround the power output main shaft 2 and are arranged in a circular shape
  • the power output main shaft 2 is located at the centre of the respective pneumatic motor stages
  • one gear shaft of each pair of motor gear stages is the power output shaft of each pneumatic motor stage
  • the power output shafts of the first pneumatic motor stage, the second pneumatic motor stage and the third pneumatic motor stage are connected with the power output main shaft 2 through a transmission gear.
  • the transmission gear comprises a driving gear 113, 123, 133 provided on the power output shaft 112, 122, 132 of each pneumatic motor stage and a driven gear 21 provided on the power output main shaft 2 while engaging with the driving gear 113, 123, 133 of each pneumatic motor stage.
  • the driving gear 113, 123, 133 can be formed together with the power output shaft of each pneumatic motor stage, so that the power output shaft of each pneumatic motor stage becomes a driving gear shaft, and the driving gears 113, 123, 133 on the driving gear shafts of respective motor stages have the same the modulus and the same number of teeth.
  • the same rotating speed of the power output shafts of the respective motor stages can be achieved by setting the number of teeth and the length of the first-stage motor gear 111, the second-stage motor gear 121 and the third-stage motor gear 131 to be the same and by increasing the modulus of the gears stage by stage.
  • Embodiment 3 it is also a three-stage pneumatic gear motor arranged in a circular shape, and its structure and the arranging manner of the respective motor stages are the same with those shown in Figs. 2 and 3 , the transmission and connection relationship between the power output shafts of the respective pneumatic motor stages and the power output main shaft is the same with the above embodiment 2, while, a difference, compared with embodiment 2, lies in the manner of achieving the same rotating speed of the power output shaft of each pneumatic gear motor stage, and embodiment 3 achieves the same rotating speed of the power output shafts of the respective motor stages by setting the modulus and the number of teeth of the first-stage motor gear 111, the second-stage motor gear 121 and the second-stage motor gear 131 to be the same and by increasing the lengths of the gears stage by stage.
  • the specific ratio relationship between the gear lengths of the respective motor gear stages 111, 121, 131 can be rendered via simple mathematic calculation according to the inverse proportion relationship between the pressure and the volume of the power gas and the pressure value of the power gas passing each motor stage.
  • Embodiment 4 it is also a three-stage pneumatic gear motor arranged in a circular shape, and its structure and the arranging manner of the respective motor stages are the same with those shown in Figs. 2 and 3 , the transmission and connection relationship between the power output shafts of the respective pneumatic motor stages and the power output main shaft is the same with the above embodiment 2, while, a difference, compared with embodiment 2, lies in the manner of achieving the same rotating speed of the power output shaft of each pneumatic gear motor stage, and embodiment 4 achieves the same rotating speed of the power output shafts of the respective motor stages by setting the modulus and the gear lengths of the first-stage motor gear 111, the second-stage motor gear 121 and the third-stage motor gear 131 to be the same and by increasing the numbers of the teeth of the gears stage by stage.
  • the specific ratio relationship between the numbers of the teeth of the respective motor gear stages 111, 121, 131 can be rendered via simple mathematic calculation according to the inverse proportion relationship between the pressure and the volume of the power gas and the pressure value of the power gas passing each motor stage.
  • the motor can be other forms of pneumatic motors; although the above embodiments of the three-stage gear motor achieve the same rotating speed delivered from the respective motor stages to the power output main shaft and then achieve the forward joining of the powers of the respective motor stages, through adjusting the rotating speeds of the power output shafts of the respective gear motor stages to be the same and through the driving gears with the same modulus and the same number of teeth, those skilled in the art would know achieving the same rotating speed delivered from the three gear motor stages to the power output main shaft through other adjusting and transmitting manners, and then to achieve the objects of the present invention, and the following embodiment 8 is one of the implementation manners.
  • Embodiment 5 illustrate the structure of a three-stage pneumatic gear motor according to the present invention, and the three-stage pneumatic gear motor comprises a shell 1 and a power output main shaft 2, and the shell 1 is provided with a gas inlet 3 and a gas outlet 4, characterized in that, the shell 1 is provided therein with three pneumatic gear motor stages, i.e., a first pneumatic gear motor stage 11 consisting of a pair of a first-stage motor gear 111, a second pneumatic gear motor stage 12 consisting of a pair of a second-stage motor gear 121 and a third pneumatic gear motor stage 13 consisting of a pair of a third-stage motor gear 131, the first pneumatic gear motor stage 11 is communicated with the gas inlet 3, the last pneumatic gear motor stage, i.e., the third pneumatic gear motor stage 13, is communicated with the gas outlet 4, and a power gas enters the shell 1 through the gas inlet 3 and then drives the first pneumatic gear motor stage 11 and then the second
  • the first pneumatic motor stage 11, the second pneumatic motor stage 12 and the third pneumatic motor stage 13 are arranged in a linear shape, one gear shaft of each pair of motor gear stages is the power output shaft of each pneumatic motor stage, the power output shafts 112, 122, 132 of the first pneumatic motor stage, the second pneumatic motor stage and the third pneumatic motor stage are connected with the power output main shaft 2 through a transmission gear, and the transmission gear comprises three first-stage driving gears 113, 123, 133 provided on the power output shafts 112, 122, 132 of each pneumatic motor stage, two first-stage driven gears 61, 62 simultaneously engaging with the first-stage driving gears of the adjacent pneumatic motor stages, two second-stage driving gear shafts 71, 72 being respectively coaxial with the two first-stage driven gears 61, 62, and one second-stage driven gear 21 simultaneously engaging with the two second-stage driving gear shafts 71, 72, and the one second-stage driven gear 21 is provided on the power output
  • the three first-stage driving gears 113, 123, 133 have the same modulus and the same number of teeth
  • the two first-stage driven gears 61, 62 have the same modulus and the same number of teeth
  • the two second-stage driving gear shafts 71, 72 have the same modulus and the same number of teeth.
  • the same rotating speed of the power output shafts of the respective motor stages can be achieved by setting the number of teeth and the length of the first-stage motor gear 111, the second-stage motor gear 121 and the third-stage motor gear 131 to be the same and by increasing the modulus of the gears stage by stage.
  • Embodiment 6 it is also a also a three-stage pneumatic gear motor arranged in a linear shape, and its structure and the arranging manner of the three motor stages are the same with those shown in Figs. 4 and 5 , the transmission and connection relationship between the power output shafts of the respective pneumatic motor stages and the power output main shaft is the same with the above embodiment 5, while, a difference, compared with embodiment 5, lies in the manner of achieving the same rotating speed of the power output shaft of each pneumatic gear motor stage, and embodiment 6 achieves the same rotating speed of the power output shafts of the respective motor stages by setting the modulus and the number of teeth of the first-stage motor gear 111, the second-stage motor gear 121 and the third-stage motor gear 131 to be the same and by increasing the gear lengths stage by stage.
  • the specific ratio relationship between the gear lengths of the respective motor gear stages 111, 121, 131 can be rendered via simple mathematic calculation according to the inverse proportion relationship between the pressure and the volume of the power gas and the pressure value of the power gas passing each motor stage.
  • Embodiment 7 it is also a also a three-stage pneumatic gear motor arranged in a linear shape, and its structure and the arranging manner of the three motor stages are the same with those shown in Figs. 4 and 5 , the transmission and connection relationship between the power output shafts of the respective pneumatic motor stages and the power output main shaft is the same with the above embodiment 5, while, a difference, compared with embodiment 5, lies in the manner of achieving the same rotating speed of the power output shaft of each pneumatic gear motor stage, and embodiment 7 achieves the same rotating speed of the power output shafts of the respective motor stages by setting the modulus and the gear lengths of the first-stage motor gear 111, the second-stage motor gear 121 and the third-stage motor gear 131 to be the same and by increasing the numbers of the teeth stage by stage.
  • the specific ratio relationship between the numbers of the teeth of the respective motor gear stages 111, 121, 131 can be rendered via simple mathematic calculation according to the inverse proportion relationship between the pressure and the volume of the power gas and the pressure value of the power gas passing each motor stage.
  • the motor can be other forms of pneumatic motors; although the above embodiments of the three-stage gear motor achieve the same rotating speed delivered from the respective motor stages to the power output main shaft and then achieve the forward joining of the powers of the respective motor stages, through adjusting the rotating speeds of the power output shafts of the respective gear motor stages to be the same and through the connection manner of the transmission gear, those skilled in the art would know achieving the same rotating speed delivered from the three gear motor stages to the power output main shaft through other adjusting manners and transmitting manners, and then to achieve the objects of the present invention.
  • Embodiment 8 this embodiment is a three-stage pneumatic gear motor arranged in a circular shape, and the arrangement of the respective pneumatic motor stages is the same with those shown in Figs. 2 and 3 , that is, the respective pneumatic motor stages surround the power output main shaft and are arranged in a circular shape, and the power output main shaft is located at the centre of the respective motor stages.
  • the transmission gear comprises respective transmission gears of the respective motor gear stages with different reduction ratios and a driven gear 21 provided at the power output main shaft 2, and thus the same rotating speed delivered from the respective pneumatic motor stages to the power output main shaft 2 is achieved, thereby achieving the invention objects of the present invention.
  • the last transmission gears of the respective pneumatic motor stages have the same modulus and the same number of teeth or different numbers of teeth, and in this way, the last one of the respective transmission gears of the respective motor gear stages with different reduction ratios can engage with the driven gear 21 at the output main shaft 2.
  • the rotating speeds of the respective motor gear stages have been adjusted to be the same through the respective transmission gears with different reduction ratios before the last transmission gears; when the last transmission gears have different numbers of teeth, the rotating speeds of the respective motor gear stages have not been adjusted to be the same through the respective transmission gears with different reduction ratios before the last transmission gears, and the rotating speeds delivered to the output main shaft 2 must be adjusted to be the same through the relationship between the numbers of the teeth of the last transmission gears.
  • the two transmission and speed adjustment manners can both achieve the object of achieving the same rotating speed delivered from the respective pneumatic motor stages to the output main shaft 2.
  • the above embodiments of the present invention can all improve the overall efficiency of the pneumatic motor, save energy, lower the noise, and then achieve the objects of the present invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gear Transmission (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Claims (8)

  1. Mehrstufiger Druckluftmotor, umfassend ein Gehäuse (1) und einer Hauptkraftabgabewelle (2), wobei das Gehäuse mit einem Gaseinlass (3) und einem Gasauslass (4) versehen ist,
    wobei zwei oder mehr Druckluftmotorstufen in dem Gehäuse (1) installiert sind, wobei die erste Druckluftmotorstufe (11) der zwei oder mehr Druckluftmotorstufen mit dem Gaseinlass (3) in Verbindung steht, und die letzte Druckluftmotorstufe mit dem Gasauslass (4) in Verbindung steht, ein Antriebsgas durch den Gaseinlass in das Gehäuse (1) eintritt, die erste Druckluftmotorstufe (12) und dann die nächste Druckluftmotorstufe antreibt, und schließlich (4) durch den Gasauslass aus dem Gehäuse (1) ausgestoßen wird, wobei jede Druckluftmotorstufe mit einer Kraftabgabewelle versehen ist, die mit der Hauptkraftabgabewelle (2) verbunden ist, so dass die von allen Druckluftmotorstufen erzeugten Leistungen miteinander vereint und dann von der Hauptkraftabgabewelle (2) übertragen werden; wobei die Drehgeschwindigkeiten, die von den Kraftabgabewellen jeder Stufe des Druckluftmotors an die Hauptkraftabgabewelle (2) übertragen werden, gleich sind, so dass die von jeder Stufe des Druckluftmotors erzeugten Leistungen nach vorne vereint und dann von der Hauptkraftabgabewelle (2) ausgegeben werden; wobei der Druckluftmotor ein Getriebemotor ist, und wobei das Gehäuse (1) darin mit einer ersten Druckluftmotorstufe (11), bestehend aus einem erststufigen Motorzahnradpaar (111), einer zweiten Druckluftmotorstufe (12), bestehend aus einem zweitstufigen Motorzahnradpaar (121), und einer dritten Druckluftmotorstufe, bestehend aus einem drittstufigen Motorzahnradpaar, versehen ist, und die Kraftabgabewellen der ersten Druckluftmotorstufe, der zweiten Druckluftmotorstufe und der dritten Druckluftmotorstufe mit der Hauptkraftabgabewelle (2) über ein Getriebe verbunden sind, dadurch gekennzeichnet, dass die erste Druckluftmotorstufe (11), die zweite Druckluftmotorstufe (12) und die dritte Druckluftmotorstufe (13) die Hauptkraftabgabewelle (2) umgeben und kreisförmig angeordnet sind, wobei die Hauptkraftabgabewelle (2) in der Mitte der jeweiligen Druckluftmotorstufen angeordnet ist, eine Getriebewelle jedes Paars von Motorgetriebestufen die Kraftabgabewelle jeder Druckluftmotorstufe ist, und das Getriebe ein antreibendes Zahnrad, welches auf der Kraftabgabewelle jeder Druckluftmotorstufe vorgesehen ist, und ein angetriebenes Zahnrad umfasst, das auf der Hauptkraftabgabewelle vorgesehen ist, während der Eingriff mit dem antreibenden Zahnrad jeder Druckluftmotorstufe erfolgt.
  2. Mehrstufiger Druckluftmotor nach Anspruch 1, dadurch gekennzeichnet, dass das auf der Kraftabgabewelle jeder Druckluftmotorstufe vorgesehene, antreibende Zahnrad ein auf der Kraftabgabewelle ausgebildetes Zahnrad ist, so dass die Kraftabgabewelle jeder Druckluftmotorstufe zu einer Antriebswelle wird, und die antreibenden Zahnräder auf den Antriebswellen entsprechender Druckluftmotorstufen denselben Modul und dieselbe Zähnezahl aufweisen.
  3. Mehrstufiger Druckluftmotor nach Anspruch 1, dadurch gekennzeichnet, dass die erste Druckluftmotorstufe (11), die zweite Druckluftmotorstufe (12) und die dritte Druckluftmotorstufe (13) in linearer Form angeordnet sind, wobei eine Getriebewelle jedes Paars von Motorgetriebestufen die Kraftabgabewelle jeder Druckluftmotorstufe ist, wobei das Getriebe drei erststufige antreibende Zahnräder (113, 123, 133), die auf der Kraftabgabewelle (112, 122, 132) jeder Druckluftmotorstufe vorgesehen sind, zwei erststufige angetriebene Zahnräder, die gleichzeitig mit den erststufigen antreibenden Zahnrädern der benachbarten Druckluftmotorstufen in Eingriff stehen, zwei zweitstufige antreibende Getriebewellen, die jeweils koaxial zu den zwei zweitstufigen angetriebenen Zahnrädern verlaufen, und ein zweitstufiges angetriebenes Zahnrad, das gleichzeitig mit den zwei zweitstufigen Antriebswellen in Eingriff steht, umfasst, und das eine zweitstufige angetriebene Zahnrad auf der Hauptkraftabgabewelle (2) vorgesehen ist.
  4. Mehrstufiger Druckluftmotor nach Anspruch 3, dadurch gekennzeichnet, dass die drei erststufigen antreibenden Zahnräder (113, 123, 133) denselben Modul und dieselbe Zähnezahl aufweisen, die zwei erststufigen angetriebenen Zahnräder denselben Modul und dieselbe Zähnezahl aufweisen, und die zwei zweitstufigen Antriebswellen denselben Modul und dieselbe Zähnezahl aufweisen.
  5. Mehrstufiger Druckluftmotor nach Anspruch 2 oder 4, dadurch gekennzeichnet, dass das erststufige Motorgetriebe, das zweitstufige Motorgetriebe und das drittstufige Motorgetriebe dieselbe Zähnezahl aufweisen und dieselbe Zahnradlänge aufweisen, und der Modul der Zahnräder von Stufe zu Stufe zunimmt, so dass die Drehgeschwindigkeiten der Kraftabgabewellen der jeweiligen Druckluftmotorstufen gleich sind.
  6. Mehrstufiger Druckluftmotor nach Anspruch 2 oder 4, dadurch gekennzeichnet, dass das erststufige Motorgetriebe, das zweitstufige Motorgetriebe und das drittstufige Motorgetriebe dieselbe Zähnezahl und denselben Modul aufweisen und die Länge der Zahnräder von Stufe zu Stufe zunehmen, so dass die Drehgeschwindigkeiten der Kraftabgabewellen der jeweiligen Druckluftmotorstufen gleich sind.
  7. Mehrstufiger Druckluftmotor nach Anspruch 2 oder 4, dadurch gekennzeichnet, dass das erststufige Motorgetriebe, das zweitstufige Motorgetriebe und das drittstufige Motorgetriebe denselben Modul und dieselbe Zahnradlänge aufweisen, und die Zähnezahl der Zahnräder von Stufe zu Stufe zunimmt, so dass die Drehgeschwindigkeiten der Kraftabgabewellen der jeweiligen Druckluftmotorstufen gleich sind.
  8. Mehrstufiger Druckluftmotor nach Anspruch 1, dadurch gekennzeichnet, dass die erste Druckluftmotorstufe, die zweite Druckluftmotorstufe und die dritte Druckluftmotorstufe die Hauptkraftabgabewelle umgeben und kreisförmig angeordnet sind, wobei sich die Hauptkraftabgabewelle in der Mitte der jeweiligen Druckluftmotorstufen befindet, wobei eine Getriebewelle jedes Paars von Motorgetriebestufen die Kraftabgabewelle jeder Druckluftmotorstufe ist, wobei das Getriebe entsprechende Getriebe der jeweiligen Motorgetriebestufen mit unterschiedlichen Untersetzungsverhältnissen umfasst, und ein angetriebenes Zahnrad auf der Hauptkraftabgabewelle vorgesehen ist, und die von den jeweiligen Druckluftmotorstufen an die Hauptkraftabgabewelle übertragenen Drehgeschwindigkeiten gleich sind.
EP10851297.1A 2010-05-13 2010-11-15 Mehrstufiger pneumatikmotor Not-in-force EP2570590B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201010170599.5A CN101852091A (zh) 2010-05-13 2010-05-13 一种节能高效的气动马达
PCT/CN2010/078715 WO2011140793A1 (zh) 2010-05-13 2010-11-15 多级气动马达

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EP2570590A1 EP2570590A1 (de) 2013-03-20
EP2570590A4 EP2570590A4 (de) 2017-05-17
EP2570590B1 true EP2570590B1 (de) 2018-07-11

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US (1) US20130055884A1 (de)
EP (1) EP2570590B1 (de)
CN (3) CN101852091A (de)
AU (1) AU2010353176B2 (de)
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WO (1) WO2011140793A1 (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101852091A (zh) * 2010-05-13 2010-10-06 石家庄中煤装备制造有限公司 一种节能高效的气动马达
US10641239B2 (en) 2016-05-09 2020-05-05 Sunnyco Inc. Pneumatic engine and related methods
US10465518B2 (en) * 2016-05-09 2019-11-05 Sunnyco Inc. Pneumatic engine and related methods
CN110159351B (zh) * 2019-06-03 2024-04-23 鹤飞机械有限公司 内曲线齿轮式气动马达执行器
CN111120299A (zh) * 2019-12-11 2020-05-08 清远市高新精旺新能源研究院有限公司 一种输送低黏度废液齿轮泵
CN112535911B (zh) * 2020-08-28 2022-10-18 深圳中科飞测科技股份有限公司 光学设备及其工作方法

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1223876A (en) * 1916-01-05 1917-04-24 Morris A Heimann Motor and support for display-forms and the like.
US2631428A (en) * 1946-08-28 1953-03-17 Arthur H Nelson Multiple fluid-operated rotary gear motors with treatment between stages
US2463349A (en) * 1948-01-20 1949-03-01 Rawlings R Baner Electric motor assembly
US3015283A (en) * 1958-11-24 1962-01-02 Bayer Ag Gear pumps and motors
GB999459A (en) * 1961-04-19 1965-07-28 Erich Martin Improvements in and relating to multi-stage rotary engines
US3724427A (en) * 1971-06-15 1973-04-03 K Sauder Rotary internal combustion engine
US3782340A (en) * 1972-02-04 1974-01-01 J Nam Gear-type rotary engine
US4386893A (en) * 1981-05-04 1983-06-07 Deere & Company Gear pump or motor with a shaftless gear
US4668159A (en) * 1985-07-19 1987-05-26 Biordo Jose M Compressed rotative motor
SU1722239A4 (ru) * 1990-04-17 1992-03-23 И.Ф.Суслов Силова многоагрегатна установка
DE4216989C2 (de) * 1992-05-22 1998-06-04 Gottfried Baehr Motor mit sehr hohem Drehmoment
CN1041647C (zh) * 1995-09-05 1999-01-13 夏琼辉 燃烧火药旋转发动机
DE19849805C1 (de) * 1998-10-29 2000-03-09 Voith Turbo Kg Baureihe für Zahnradmotoren mit unterschiedlich theoretisch abgebbarem Drehmoment und Verfahren zur Herstellung der einzelnen Zahnradmotoren der Baureihe
JP2002031199A (ja) * 2000-07-18 2002-01-31 Honda Motor Co Ltd 変速機
US6450448B1 (en) * 2001-08-17 2002-09-17 Toshimi Suzuki Airplane wheel unit
WO2005005781A1 (en) * 2003-07-14 2005-01-20 Elthom Enterprises Limited Volume screw machine of rotary type
CN2702088Y (zh) * 2004-03-26 2005-05-25 朱妙睿 同轴多节单螺杆式空气压缩机
WO2009034421A1 (en) * 2007-09-13 2009-03-19 Ecole polytechnique fédérale de Lausanne (EPFL) A multistage hydro-pneumatic motor-compressor
CN101761360A (zh) * 2008-12-24 2010-06-30 徐开文 多段式齿轮动力装置
CN101852091A (zh) * 2010-05-13 2010-10-06 石家庄中煤装备制造有限公司 一种节能高效的气动马达
CN201696097U (zh) * 2010-05-13 2011-01-05 石家庄中煤装备制造有限公司 一种节能高效的气动马达

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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AU2010353176A1 (en) 2012-12-06
AU2010353176B2 (en) 2013-10-17
CN102003215A (zh) 2011-04-06
EP2570590A4 (de) 2017-05-17
EP2570590A1 (de) 2013-03-20
US20130055884A1 (en) 2013-03-07
WO2011140793A1 (zh) 2011-11-17
CN102003215B (zh) 2013-05-15
CN101852091A (zh) 2010-10-06
RU2012148187A (ru) 2014-06-20
CN201843645U (zh) 2011-05-25

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