CN215805014U

CN215805014U - Air supply machine

Info

Publication number: CN215805014U
Application number: CN202120690756.9U
Authority: CN
Inventors: 刘贵文; 毋宏兵
Original assignee: Positec Power Tools Suzhou Co Ltd
Current assignee: Positec Power Tools Suzhou Co Ltd
Priority date: 2020-04-03
Filing date: 2021-04-06
Publication date: 2022-02-11
Anticipated expiration: 2031-04-06
Also published as: CN113494437A; WO2021197490A1

Abstract

The application discloses air feeder includes: a housing; a motor located within the housing; a compression assembly including a cylinder and a piston disposed within the cylinder; the driving assembly is used for converting the rotating motion of the motor shaft into the reciprocating motion of the piston in the cylinder, and comprises a speed reducing mechanism, wherein the speed reducing mechanism is used for reducing the rotating speed of the motor shaft and driving the piston to reciprocate through an output shaft of the speed reducing mechanism so as to compress air; the inner diameter of the cylinder is 50 mm to 100 mm, and the stroke of the piston is 40 mm to 100 mm; the rotating speed range of the output shaft is 60 rpm-600 rpm. This air feeder has designed the diameter of cylinder, the rotational speed of stroke and output shaft optimally, and then has made the single compressed air volume big, and the rotational speed reduces under the unchangeable circumstances of total discharge capacity, so makes the time of air compression process in the cylinder elongate, and the heat dissipation accelerates, and then approaches isothermal compression, promotes air compression efficiency.

Description

Air supply machine

Technical Field

The present application relates to air feeders.

Background

The atmospheric (below 0.8 Mpa) pneumatic tool still applies to the use occasion of various pneumatic tools in a large number because of its simple structure, reliable operation, easy maintenance, advantage such as longe-lived, for example: pneumatic nail rifle, spray gun, wind big gun, gas are cut, aerating device etc. but also have some problems, and its air supply air feeder is heavy to be carried inconveniently, and can not the cordless operation, and factors such as inconvenient are often connected to the building site power, cause the user to complain about experience and feel not good. Therefore, various lithium battery air compressors have appeared in the market to meet such market demands, and the development of the lithium battery air compressors is strong.

Although this type of air supply machine has solved the power supply problem, the weight is still generally heavy due to the gas storage tank and the structure, and the portability is not realized at all, and because of adopting the small-volume high-frequency compression technology, the compression efficiency is low, the heat generation is serious and the vibration and the noise are also large.

SUMMERY OF THE UTILITY MODEL

In view of the above-mentioned shortcomings, it is an object of the present application to provide an air supply machine to improve air compression efficiency.

In order to achieve the purpose, the technical scheme is as follows: an air feeder, comprising: a housing; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis; a battery pack connected to the case; a compression assembly including a cylinder and a piston disposed within the cylinder; the driving assembly is used for converting the rotating motion of the motor shaft into the reciprocating motion of the piston in the cylinder and comprises a speed reducing mechanism, and the speed reducing mechanism is used for reducing the rotating speed of the motor shaft and driving the piston to reciprocate through an output shaft of the speed reducing mechanism; the inner diameter of the cylinder is 50 mm to 100 mm, and the stroke of the piston is 40 mm to 100 mm; the rotating speed range of the output shaft is 60 rpm-600 rpm.

The application provides an air feeder has designed the diameter of cylinder, the rotational speed of stroke and output shaft optimally, and then makes single compressed air volume big, and the rotational speed reduces under the unchangeable condition of total discharge capacity, so makes the time of air compression process in the cylinder elongate, and the heat dissipation accelerates, and then is close isothermal compression, and compression efficiency improves.

Preferably, the rotating speed range of the output shaft is 120 rpm-400 rpm; preferably, the rotating speed range of the output shaft is 180 rpm-250 rpm; preferably, the rotation speed of the output shaft ranges from 360rpm to 600 rpm.

Preferably, the inner diameter of the cylinder ranges from 50 mm to 80 mm; preferably, the piston has a stroke of 40 mm to 70 mm.

Preferably, the speed reducing mechanism is a three-stage gear speed reducing mechanism, and the total transmission ratio is 50-150. Preferably, the total transmission ratio is 50-80.

Preferably, the rated power of the motor is 600W-1200W.

Preferably, the idling speed of the motor is 18000rpm-30000 rpm. Preferably, the idling speed of the motor is 20000rpm to 30000 rpm.

Preferably, the flow rate of the compression assembly is between about 1 liter/s and 2.2 liters/s.

Preferably, the inner diameter of the cylinder ranges from 60 mm to 90 mm; the stroke of the piston is 60 mm to 90 mm;

preferably, the piston has a stroke frequency of 60 to 600 times per minute.

Preferably, the flow rate of the compression assembly is between about 1.5 liters/s and 2.2 liters/s.

Preferably, a clutch device is provided between the motor shaft and the driving assembly, the clutch device selectively transmitting power of the motor to the driving assembly.

Preferably, the air feeder further comprises an anti-reverse mechanism for causing the output shaft to rotate in one direction.

In order to achieve the purpose, the application adopts another technical scheme that: an air feeder, comprising: a housing; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis; a battery pack connected to the case; a compression assembly including a cylinder and a piston disposed within the cylinder; wherein the cylinder has an inner diameter of 50 mm to 100 mm, and the piston has a stroke of 40 mm to 100 mm; the stroke frequency of the piston is 60 to 600 times per minute; a drive assembly for converting rotational motion of the motor shaft to reciprocating motion of the piston within the cylinder.

The application provides an air feeder has designed the stroke frequency of the diameter, the stroke and the piston of cylinder optimally, and then makes single compressed air big, and the rotational speed reduces under the unchangeable circumstances of total discharge capacity, so makes the time of air compression process in the cylinder elongate, and the heat dissipation accelerates, and then is close isothermal compression, and compression efficiency improves.

In order to achieve the purpose, the application adopts another technical scheme that: an air feeder, comprising: a housing; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis; a battery pack connected to the case; a compression assembly including a cylinder and a piston disposed within the cylinder; the driving assembly is used for converting the rotating motion of the motor shaft into the reciprocating motion of the piston in the cylinder and comprises a speed reducing mechanism, and the speed reducing mechanism is used for reducing the rotating speed of the motor shaft and driving the piston to reciprocate through an output shaft of the speed reducing mechanism; the total transmission ratio of the speed reducing mechanism is 50-150; the inner diameter of the cylinder is 50 mm to 100 mm, and the stroke of the piston is 40 mm to 100 mm.

The application provides an air feeder has designed the diameter of cylinder, stroke and reduction gears's total drive ratio optimally, and then makes single compressed air volume big, and the rotational speed reduces under the unchangeable circumstances of total discharge capacity, so makes the air lengthen in the time of compression process in the cylinder, and the heat dissipation accelerates, and then is close isothermal compression, and compression efficiency improves.

In order to achieve the purpose, the application adopts another technical scheme that: an air feeder, comprising: a housing; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis, and the motor having an idle speed in a range of 18000rpm to 30000 rpm; a compression assembly including a cylinder and a piston disposed within the cylinder; the driving assembly is used for converting the rotating motion of the motor shaft into the reciprocating motion of the piston in the cylinder and comprises a speed reducing mechanism, and the speed reducing mechanism is used for reducing the rotating speed of the motor shaft of the motor and driving the piston to reciprocate through an output shaft of the speed reducing mechanism; the cylinder has an inner diameter ranging from 50 mm to 80 mm, and the piston has a stroke ranging from 40 mm to 70 mm.

The air supply machine provided by the application adopts the high-speed motor, so that the weight of the whole machine is greatly reduced; the diameter and the stroke of the air cylinder are optimally designed, the single air compression amount is large, and the rotating speed is reduced under the condition that the total displacement is not changed, so that the time of the air in the air cylinder in the compression process is prolonged, the heat dissipation is accelerated, the isothermal compression is further approached, and the compression efficiency is improved;

another object of the present application is to provide an air feeder that is lightweight and also has a high flow rate.

In order to achieve the purpose, the technical scheme is as follows: an air feeder, comprising: a housing; a battery pack connected to the case; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis, and an idle speed of the motor ranging from 20000rpm to 30000 rpm; a battery pack connected to the case; a compression assembly including a cylinder and a piston disposed within the cylinder; the driving assembly is used for converting the rotating motion of the motor shaft into the reciprocating motion of the piston in the cylinder and comprises a speed reducing mechanism, and the speed reducing mechanism is used for reducing the rotating speed of the motor shaft of the motor and driving the piston to reciprocate through an output shaft of the speed reducing mechanism; wherein the flow rate of the compression assembly is between about 1 liter/s and 2.2 liters/s.

The air feeder provided by the application adopts the high-speed motor, reduces the weight of the whole machine and simultaneously has higher flow rate.

Preferably, the inner diameter of the cylinder ranges from 50 mm to 80 mm; the piston stroke is 40 mm to 70 mm.

Another object of the present application is to provide an air feeder that optimally designs the ratio of the single-stroke displacement of the cylinder with respect to the rated power.

The adopted technical scheme is as follows: an air feeder, comprising: a housing; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis; a battery pack connected to the case; the compression assembly comprises a cylinder and a piston arranged in the cylinder; a drive assembly for converting rotational motion of the motor shaft into reciprocating motion of the piston within the cylinder; each cylinder has a single stroke displacement of 150-250 ml; the rated power of the motor is within 1200W, and the proportion of the single-stroke displacement of each cylinder relative to the rated power is 0.18cm³from/W to 0.42cm³/W。

Preferably, the driving assembly comprises a speed reducing mechanism, and the speed reducing mechanism is used for reducing the rotating speed of the motor shaft and driving the piston to reciprocate through an output shaft of the speed reducing mechanism; the rotating speed range of the output shaft is 60 rpm-600 rpm.

Preferably, the rotation speed of the output shaft ranges from 360rpm to 600 rpm.

Another object of the present application is to provide a gas feeder with low energy consumption and high gas feeding efficiency.

In order to achieve the purpose, the technical scheme is as follows: an air feeder, comprising: a housing; a battery pack connected to the case; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis, the motor having a power ratingWithin 1200W; a compression assembly including a cylinder and a piston disposed within the cylinder; a drive assembly for converting rotational motion of the motor shaft to reciprocating motion of the piston within the cylinder; wherein a ratio of a flow rate of the compression assembly to the rated power is not less than 1.18cm³/S/W。

Wherein the ratio of the flow rate of the compression assembly relative to the rated power is at 1.25cm³(ii)/S/W to 2.75cm³/S /W。

Preferably, the ratio of the flow rate of the compression assembly with respect to said nominal power is at 1.3cm³(ii)/S/W to 2.3cm³/S/W。

The air feeder provided by the application optimally designs the ratio of the flow rate of the compression assembly relative to the rated power, and can not reduce the air supply amount under the condition of improving the endurance capacity (low energy consumption) of the battery pack, thereby providing the air feeder with low energy consumption and large discharge capacity.

It is another object of the present application to provide a gas feeder that is lightweight to improve portability.

In order to achieve the purpose, the technical scheme of the application is as follows: an air feeder, comprising: a housing; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis; a compression assembly including a cylinder and a piston disposed within the cylinder; a drive assembly for converting rotational motion of the motor shaft to reciprocating motion of the piston within the cylinder; wherein the weight of the air feeder is less than 6kg for a rated power within 1200W.

Preferably, the driving assembly comprises a speed reducing mechanism, the speed reducing mechanism is used for reducing the rotating speed of a motor shaft of the motor and driving the piston to reciprocate through an output shaft of the speed reducing mechanism, and the rotating speed of the output shaft is less than 600 rpm. Preferably, the rotation speed of the output shaft is 360rpm to 600 rpm.

Preferably, the air feeder weighs 3kg to 5 kg. Preferably, the air feeder weighs between 4kg and 5.5 kg.

Another object of the present application is to provide an air feeder that is portable and has good performance. In order to achieve the purpose, the technical scheme of the application is as follows: an air feeder, comprising: a housing; a battery pack connected to the case; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis; a compression assembly including a cylinder and a piston disposed within the cylinder; a drive assembly for converting rotational motion of the motor shaft to reciprocating motion of the piston within the cylinder; wherein, for rated power within 1200W, the ratio of the weight of the air feeder to the rated power is not more than 7.5 g/W.

Preferably, the ratio of the weight of the air feeder to the rated power is between 4.38g/W and 7.5 g/W. Preferably, the ratio of the weight of the air feeder to the rated power is between 3.8g/W and 6.2 g/W.

The air feeder that this application provided has designed the weight of air feeder optimally to the proportion of rated power, and then makes under the not influenced circumstances of performance of air feeder, and complete machine weight is lighter portable.

It is another object of the present application to provide an air supply machine that is portable and has a large flow rate. In order to achieve the purpose, the technical scheme of the application is as follows: an air feeder, comprising: a housing; a battery pack connected to the case; a motor located within the housing; a compression assembly including a cylinder and a piston disposed within the cylinder; a drive assembly for converting rotational motion of the motor shaft to reciprocating motion of the piston within the cylinder; the ratio of the flow rate of the compression assembly relative to the weight of the air feeder is not less than 0.16 liters/s/kg.

Preferably, the ratio of the flow rate of the compression assembly relative to the weight of the air feeder is in the range of 0.2 liters/s/kg to 0.7 liters/s/kg. Preferably, the ratio of the flow rate of the compression assembly relative to the weight of the air feeder is in the range of 0.25 liters/s/kg to 0.4 liters/s/kg.

The air feeder that this application provided has designed the proportion of the flow rate of compression subassembly for the weight of air feeder optimally, and then makes air feeder complete machine weight lighter, portable, and the flow rate can satisfy the air feed demand moreover.

Another object of the present application is to provide an air feeder having a long service life. In order to achieve the purpose, the technical scheme of the application is as follows: an air feeder, comprising: a housing; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis; a compression assembly including a cylinder and a piston disposed within the cylinder; a drive assembly for converting rotational motion of the motor shaft to reciprocating motion of the piston within the cylinder; and a clutch device is arranged between the motor shaft and the driving component, and the clutch device enables the motor shaft to selectively drive the driving component to move.

Be provided with clutch in this application, the motor operation in-process selects whether to transmit power to drive assembly through clutch. Therefore, according to the actual working condition of the pneumatic tool, the power transmission can be switched off or on without turning off the motor, and the motor cannot be started frequently, so that the service life of the air feeder is ensured.

Preferably, the clutch device includes a first clutch supported by the motor shaft, a second clutch provided with a driving member engaged with the driving assembly, and a moving assembly urging the second clutch and the first clutch to be engaged and disengaged. When the second clutch piece is engaged with the first clutch piece, the power of the motor is transmitted to the driving assembly, and then the piston moves to compress air; when the second clutch piece is separated from the first clutch piece, the power of the motor cannot be transmitted to the driving assembly, and the motor idles.

Preferably, the first clutch is fixed to a motor shaft of the motor, and the moving assembly causes the second clutch to move along the motor axis to engage and disengage the first clutch.

Preferably, the housing includes a clutch housing accommodating the clutch device, the moving assembly includes a stationary raceway disc, a moving raceway disc and a raceway steel ball which are arranged on the clutch housing, wherein the moving raceway disc and the stationary raceway disc are provided with raceways for accommodating the raceway steel ball, the raceways are spiral raceways, and when the moving raceway disc rotates, the moving raceway disc axially moves under the action of the steel ball, so that the second clutch member is engaged with and disengaged from the first clutch member.

Preferably, the moving assembly further comprises a solenoid, an iron core accommodated in the solenoid, and a connecting element connecting the iron core and the moving rolling way disc, wherein the solenoid is electrified to drive the iron core to move axially along the solenoid, and further pull the moving rolling way disc to rotate.

Preferably, the moving assembly further includes a return mechanism including a return spring providing a spring force to move the second clutch member in a direction to disengage from the first clutch member.

Preferably, the reset mechanism further comprises a limiting part, the reset spring is arranged between the limiting part and the second clutch part, and a limiting steel ball is arranged between the limiting part and the motor shaft.

Preferably, a thrust bearing is provided between the moving race disc and the second clutch member. Preferably, the first clutch member is a flywheel. Therefore, the flywheel can store energy when the motor idles, and the loaded starting is realized.

Preferably, the first clutch member is provided with a friction ramp for driving the second clutch member.

Preferably, the slope of the friction ramp is 3 (multiplication factor).

Preferably, the multiplication factor of the clutch device is 20.

Preferably, the second clutch member is slidably disposed on the motor shaft through a needle bearing.

In order to achieve the purpose, the application adopts another technical scheme that: an air feeder, comprising: a housing; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis; a compression assembly including a cylinder and a piston disposed within the cylinder; a drive assembly for converting rotational motion of the motor shaft to reciprocating motion of the piston within the cylinder; a pressure sensor for detecting a pressure value of gas discharged from the cylinder; the clutch device is arranged between the motor shaft and the driving assembly and comprises a first clutch piece and a second clutch piece, when the pressure value is lower than a preset lowest value, the first clutch piece and the second clutch piece are engaged, and the clutch device transmits the power of the motor to the driving assembly; when the pressure value is higher than a preset highest value, the first clutch piece and the second clutch piece are separated, and the clutch device cannot transmit the power of the motor to the driving assembly.

Preferably, the air feeder comprises a buffer pipe communicated with the air cylinder, and the pressure sensor is used for detecting the pressure value of the air pressure in the buffer pipe.

Preferably, the capacity of the buffer pipe is equivalent to the capacity of the cylinder. Preferably, the buffer pipe is provided with at least one of a safety valve, a quick connector and a pressure gauge.

Preferably, the clutch device comprises a pull-up electromagnet, and when the pressure value is lower than the preset lowest value, the first clutch member and the second clutch member are engaged by electrifying the pull-up electromagnet; and when the pressure value is higher than the preset highest value, the pull-up electromagnet is powered off, and the first clutch piece and the second clutch piece are separated.

It is another object of the present application to provide a gas supply machine that provides single pack capability.

In order to achieve the purpose, the technical scheme of the application is as follows: an air feeder, comprising: a housing; a battery pack connected to the case; a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis; a compression assembly including a cylinder and a piston disposed within the cylinder; a drive assembly for converting rotational motion of the motor shaft to reciprocating motion of the piston within the cylinder; the driving assembly comprises a speed reducing mechanism, and the speed reducing mechanism is used for reducing the rotating speed of a motor shaft of the motor and driving the piston to reciprocate through an output shaft of the speed reducing mechanism; and the anti-reverse mechanism is positioned in the shell and is used for enabling the output shaft to rotate in one direction.

The application provides an anti-reverse mechanism, can make the compression unit area carry and stop when certain random position, also can be because connecting rod crank mechanism reverses. The pressurized high-pressure gas is prevented from being changed into low-pressure gas. Thereby avoiding the waste of the power of the battery pack and improving the single-pack capacity.

Preferably, the anti-reverse mechanism includes a one-way clutch provided on the output shaft.

Preferably, the one-way clutch includes a one-way needle bearing, an inner ring of the one-way needle bearing is fixedly connected with the output shaft, and an outer ring of the one-way needle bearing is fixedly connected with the housing.

Preferably, the anti-reverse mechanism comprises a one-way needle bearing, an inner ring of the one-way needle bearing is fixedly connected with the output shaft, and an outer ring of the one-way needle bearing is fixedly connected with the shell.

Preferably, a clutch device is arranged between the motor shaft and the driving assembly, and the clutch device enables the motor shaft to selectively drive the driving assembly to move.

It is another object of the present application to provide a plug and play, on demand air feeder.

In order to achieve the purpose, the technical scheme of the application is as follows: an air feeder, comprising: a housing; a motor located within the housing; a compression assembly including a cylinder and a piston disposed within the cylinder; a clutch device having an engaged state in which power of the motor is transmitted to the compression mechanism and a disengaged state in which power of the motor is not transmitted to the compression mechanism; a battery pack detachably attached to the housing; a pressure sensor capable of generating a pressure signal related to an outlet pressure value of the air feeder; a controller electrically connected to the battery pack, the controller for controlling the air feeder to operate: receiving the pressure signal from the pressure sensor, comparing an outlet pressure value of the gas feeder from the pressure signal with a preset pressure value, wherein the preset pressure value comprises a preset lowest value and a preset highest value, and when the pressure value is higher than the preset highest value, the controller controls the clutch device to be in a separation state; when the pressure value is lower than the preset minimum value, the controller controls the clutch device to be in an engaged state.

Preferably, when the pressure value is lower than the preset lowest value, the controller controls the motor to start first, and then controls the clutch device to be in the engaged state.

In order to realize the purpose, another technical scheme is as follows: an air feeder, characterized in that: the air feeder includes: a housing; a motor located within the housing; a compression assembly including a cylinder and a piston disposed within the cylinder; a clutch mechanism having an engaged state in which power of the motor is transmitted to the compression mechanism and a disengaged state in which power of the motor is not transmitted to the compression mechanism; the clutch mechanism comprises a pull-in electromagnet; a battery pack detachably attached to the housing; a pressure sensor capable of generating a pressure signal related to an outlet pressure value of the air feeder; a controller electrically connected to the battery pack, the controller for controlling the air feeder to operate: receiving the pressure signal from the pressure sensor, comparing an outlet pressure value of the inflator from the pressure signal with a preset pressure value, wherein the preset pressure value comprises a preset lowest value and a preset highest value, and when the pressure value is higher than the preset highest value, the controller controls the pull electromagnet to be powered off; and when the pressure value is lower than the preset lowest value, the controller controls the pull-up electromagnet to be electrified.

The application also provides an air feeder, includes: a compression assembly for compressing air; the compression assembly comprises a cylinder and a piston which is arranged in the cylinder and is in sliding fit with the cylinder; the inner diameter of the cylinder ranges from 50 mm to 100 mm, and the stroke of the piston ranges from 40 mm to 100 mm; a drive assembly for driving the piston; the driving assembly comprises a motor and a transmission mechanism; the motor is provided with an output shaft; the transmission mechanism is used for converting the rotary motion of an output shaft of the motor into the reciprocating motion of the piston and compressing air; the motor is a brushless non-inductive high-speed motor.

Preferably, the cylinder is communicated with a cache pipe for storing compressed gas, and the cache pipe is provided with a pressure sensor for internal air pressure and a quick connector; the outer diameter of the buffer pipe is smaller than the inner diameter of the cylinder.

Preferably, a clutch device is further arranged between the motor and the transmission mechanism; the clutch device is used for allowing the motor to transmit power when the air pressure of the cache pipe is lower than a preset pressure and cutting off the motor to transmit power when the air pressure of the cache pipe is higher than the preset pressure.

Preferably, the transmission mechanism includes a speed reduction mechanism; the speed reducing mechanism is used for reducing the rotating speed of an output shaft of the motor and driving the piston through the output shaft of the speed reducing mechanism; the speed of the output shaft of the speed reducing mechanism is below 600rpm, and the speed reducing mechanism adopts a multi-stage planetary speed reducing mechanism.

Preferably, the air feeder has a controller; the controller is connected with the pressure sensor and the clutch device, and the controller controls the on and off of the clutch device through the detection pressure of the pressure sensor.

Preferably, the clutch device includes: the device comprises a first clutch piece, a second clutch piece, a movable raceway disc, a static raceway disc, raceway steel balls and a reset mechanism; the first clutch is fixed on an output shaft of the motor; the static raceway disc is fixed, the movable raceway disc and the movable raceway disc are arranged oppositely, and raceways for accommodating the raceway steel balls are arranged on the movable raceway disc and the static raceway disc; the movable roller path disc enables the second clutch to be engaged and disengaged with the first clutch through reciprocating rotation; the reset mechanism is used for resetting the clutch piece to an initial position.

Preferably, the clutch device includes: the first clutch piece and the second clutch piece adopt a mode that friction surfaces are inclined surfaces. Preferably, the first clutch member is a flywheel fixedly sleeved outside the output shaft of the motor.

Preferably, the reset mechanism comprises: the device comprises a return spring, a limiting steel ball, a steel ball limiting cover, a thrust bearing and a needle bearing; the thrust bearing is positioned between the second clutch piece and the movable raceway disc; the return spring, the limiting steel ball and the steel ball limiting cover are positioned in the second clutch piece; one end of the reset spring is abutted against the second clutch piece, and the other end of the reset spring is abutted against the steel ball limiting cover; the limiting steel ball is arranged in the steel ball limiting cover and is abutted against the output shaft of the motor.

Preferably, the movable roller path disc is provided with a boss connector, the boss connector is connected with one end of a pull cable, and the other end of the pull cable is connected with the iron core; the controller is connected with a pull-in electromagnet for pulling the iron core; the controller controls the on-off of the pull-up electromagnet through the detection pressure of the pressure sensor.

The air feeder that this application embodiment provided is through adopting noninductive brushless high speed motor, and the cylinder adopts major diameter, the long stroke, and then the single compressed air volume is big, and corresponding rotational speed reduces under the unchangeable circumstances of total discharge capacity, so makes the time of air compression process in the cylinder elongate, and the heat dissipation accelerates, and then is close isothermal compression, and compression efficiency improves.

Specific embodiments of the present invention are disclosed in detail with reference to the following description and drawings, indicating the manner in which the principles of the utility model may be employed. It should be understood that the embodiments of the utility model are not so limited in scope.

Features that are described and/or illustrated with respect to one embodiment may be used in the same way or in a similar way in one or more other embodiments, in combination with or instead of the features of the other embodiments.

It should be emphasized that the term "comprises/comprising" when used herein, is taken to specify the presence of stated features, integers, steps or components but does not preclude the presence or addition of one or more other features, integers, steps or components.

Drawings

Figure 1 is a schematic perspective view of a gas feeder according to one embodiment of the present application;

FIG. 2 is another view of FIG. 1;

FIG. 3 is a schematic cross-sectional view of FIG. 1

FIG. 4 is a front view of FIG. 1;

FIG. 5 is a side view of FIG. 1

FIG. 6 is a cross-sectional view of the compression assembly of FIG. 1;

FIG. 7 is an intake valve installation position view of FIG. 6;

FIG. 8 is a cross-sectional view C-C of FIG. 7;

FIG. 9 is an assembly view of the reduction mechanism, clutch device, and motor of FIG. 1;

FIG. 10 is a top view of FIG. 1;

FIG. 11 is a cross-sectional view A1-A1 of FIG. 10;

FIG. 12 is an exploded view of the clutched device of FIG. 1;

FIG. 13 is an assembly view of FIG. 12;

FIGS. 14 a-16 b are schematic views of the operation of the clutch device;

FIG. 17 is an assembly view of the reduction mechanism of FIG. 1;

FIG. 18 is a clutch structure multiplication diagram;

figure 19 is a schematic perspective view of an air feeder according to another embodiment of the present application;

FIG. 20 is a schematic view of the use state of FIG. 1;

FIG. 21 is a flow chart of the control logic of FIG. 1;

FIG. 22 is a graph of cylinder compression frequency (stroke frequency) versus cylinder jacket temperature.

Detailed Description

In order to make those skilled in the art better understand the technical solution of the present invention, the technical solution in the embodiment of the present invention will be clearly and completely described below with reference to the drawings in the embodiment of the present invention, and it is obvious that the described embodiment is only a part of the embodiment of the present invention, and not all embodiments. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, shall fall within the scope of protection of the present invention.

It will be understood that when an element is referred to as being "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may be present. The terms "vertical," "horizontal," "left," "right," and the like as used herein are for illustrative purposes only and do not represent the only embodiments.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used herein in the description of the utility model is for the purpose of describing particular embodiments only and is not intended to be limiting of the utility model. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

Please refer to fig. 1 to 18. An embodiment of the present application provides an air feeder, including: a compression assembly 100 for compressing air; the compression assembly 100 comprises a cylinder 4 and a piston 1 which is arranged in the cylinder 4 and is in sliding fit with the cylinder 4; a drive assembly for driving the piston 1; the driving assembly includes a motor 400 and a transmission mechanism; the motor 400 is provided with a motor shaft 56 rotatable about a motor axis X; the transmission mechanism is used for converting the rotary motion of the motor shaft 56 of the motor 400 into the reciprocating motion of the piston 1 for compressing air. The motor 400 is a brushless, non-inductive, high-speed motor.

In the present embodiment, the motor axis X of the motor 400 is perpendicular to the sliding direction of the piston 1; or the motor axis X of the motor 400 is perpendicular to the longitudinal direction of the cylinder 4. In the use state shown in fig. 20, the motor 400 is disposed substantially vertically as a whole above the cylinder 4. Of course, in other embodiments, the motor 400 may be disposed horizontally (horizontally), i.e., the motor axis X of the motor 400 is parallel to the sliding direction of the piston 1 (as shown in fig. 19), or parallel to the length direction of the cylinder 4. The gas supplier has a power supply to supply power to the motor 400.

Specifically, the power supply may include a battery pack 600, where the battery pack is detachably mounted to a battery pack mounting portion (not shown) of the air supply machine. The air feeder may have two battery packs 600, and the two battery packs 600 are located at both sides of the motor 400. The air feeder may also be powered by a single battery pack 600, wherein one battery pack 600 may be used as a backup and turned on to operate when another battery pack 600 is out of power. Of course, the two battery packs 600 can also be used in parallel, thus prolonging the operating time of the air feeder. The battery pack 600 may provide 20V, 40V, etc. When the power switch is turned on, the MCU of the controller 500 may detect whether the voltage of the battery pack 600 is normal, and the sampling chip collects the signal of the pressure sensor. Of course, in some embodiments, the air feeder may be provided with only a single battery pack 600, and power may be supplied using a single battery pack 600, for example, in the embodiment shown in fig. 19, where the air feeder has a single battery pack 600, the weight of the air feeder may be reduced.

As shown in fig. 6, 7 and 8, in the present embodiment, the compression assembly 100 includes a piston 1, a piston seal ring 2, a piston pin 3, a cylinder 4, a connecting rod i 5, a connecting support frame 6, a connecting rod ii 9, an intake valve 10, an outlet check valve 11 and an outlet pipe 12. The compression assembly 100 includes 2 of the cylinders 4.

Wherein, the cylinder 4 is connected with the connecting support frame 6 through a cylinder flange and a sealing ring can be arranged between the connection. The end of the cylinder 4 is provided with a nut flange for connecting the outlet check valve 11. The piston 1 is made of aluminum or plastic materials, a piston sealing ring 2 is sleeved outside the piston 1, and a specific sealing mode adopts a Y-shaped sealing ring O-shaped sealing ring or a leather cup mode. The inner surface of the cylinder 4 is hard and oxidized, the piston sealing ring 2 is arranged in the annular groove of the piston 1, and the connecting rod I5 is connected with the piston 1 through the piston pin 3. The connecting and supporting frame 6 is respectively connected with the two cylinders 4 through a flange. The drive assembly comprises a crank mechanism comprising a crank 8 and a crank pin 7. The crank 8 is hinged with two connecting rods II 9 and I5 through a crank pin 7. One end of the outlet one-way valve 11 is connected with the cylinder 4, and the other end is connected with the air outlet pipe 12.

In the present embodiment, the piston 1 is provided with an intake valve 10. Specifically, the intake valve 10 includes an intake valve plate 103 provided on the piston 1. Wherein, the piston 1 is provided with an air inlet hole 101 for air inlet and an air inlet valve plate 103 for correspondingly controlling the air inlet hole 101. An intake valve plate 103 is mounted on one side of the piston 1 by a locking screw 102. When the piston 1 compresses gas, the air inlet valve plate 103 seals the air inlet hole 101, and when the piston 1 admits air, the air inlet valve plate 103 opens the air inlet hole 101.

Wherein, the connecting support frame 6 is provided with an air inlet which is provided with an air filter 86 (see fig. 5), and the air enters the air cylinder after passing through the air filter 86. The cylinders 4 are arranged in a bilateral symmetry mode, the two cylinders 4 rotate a circle by the crank 8 and respectively compress and suck air once, the cylinders 4 are large in diameter and stroke, large in displacement of aluminum alloy or plastic cylinders, the single compression air is large, an air storage tank is not needed, and the quality of the whole machine is convenient to reduce.

The cylinder 4 provided by the embodiment adopts a large-diameter, large-stroke and large-displacement aluminum alloy or plastic cylinder, and the inner diameter of the cylinder 4 ranges from 50 mm to 100 mm. In some embodiments, the inner diameter of the cylinder 4 ranges from 50 mm to 80 mm; in some embodiments, the inner diameter of the cylinder 4 ranges from 60 mm to 90 mm. Of course, the inner diameter of the cylinder 4 may also range from 50 mm, 65 mm, 70 mm or 80 mm, etc.

The stroke of the piston 1 in the cylinder 4 is 40 mm to 100 mm. In some embodiments, the stroke of the piston 1 is 30 mm to 100 mm; in some embodiments, the stroke of the piston 1 is 40 mm to 70 mm; in some embodiments, the stroke of the piston 1 is 60 mm to 90 mm. Of course, the stroke of the piston 1 may be 50 mm, 60 mm, 65 mm, 70 mm, 80 mm, or the like.

Based on the inner diameter of the cylinder 4 and the stroke of the piston 1, accordingly, the single stroke displacement that the cylinder 4 has can be calculated according to the following formula: where V is pi r²L, where R is the radius of the cylinder 4; l is the stroke of the piston 1.

Accordingly, in some embodiments, the cylinder 4 has a single stroke displacement of between 98.13 milliliters and 785 milliliters; in some embodiments, the cylinder 4 has a single stroke displacement in the range of 100 ml to 300 ml. In some embodiments, the cylinder 4 has a single stroke displacement in the range of 150 milliliters to 250 milliliters. In the illustrated embodiment, the cylinder 4 has a single stroke displacement of about 200 milliliters.

The cylinder 4 of the air feeder of the embodiment has a large diameter and a large stroke, so that the single compression air volume is large (single stroke displacement is large), and the corresponding rotating speed is reduced under the condition that the total displacement is not changed, so that the time of the air in the compression process in the cylinder 4 is prolonged, the heat dissipation is accelerated, the isothermal compression is approached, and the compression efficiency is improved; but also reduces energy losses. If the inner diameter range and the stroke range are smaller than the ranges under the condition that the total displacement is not changed, the single-time compressed air quantity is small, and the working requirement cannot be met; if the inner diameter range and the stroke range are larger than the range, the single-time air compression amount is large, but the required motor power is also increased greatly, the volume is increased, and the whole weight of the air feeder is increased.

In some embodiments, since the battery 600 may have a rated output voltage of 20V or 40V, for example, if 2 rated output voltages are 20V battery packs or 1 rated output voltage is 40V battery pack, the ratio of the inner diameter range of the cylinder 4 to the voltage value of the power supply is: 1.5 mm per volt to 2.5 mm per volt. If 1 rated output voltage is 20V battery pack, the ratio of the inner diameter range of the cylinder 4 to the voltage value of the power supply is as follows: 2.5 mm per volt to 5 mm per volt.

The axis of the motor is the axis of the motor, but the existing portable air feeder can select a cylinder with small diameter and short stroke conventionally. The large diameter and long stroke of the cylinder require the motor to have large torque; generally, a motor with low rotating speed and large torque is heavy, so that a portable air supply machine cannot adopt the motor, and a cylinder with a single stroke and large air displacement cannot be selected.

In this embodiment, the motor 400 is a three-wire brushless non-inductive high-speed motor, which is light in weight and high in rotation speed, thereby reducing the weight of the whole air feeder. Wherein, in some embodiments, the motor 400 has an idle speed of 18000rpm to 30000 rpm. In some embodiments, the motor 400 has an idle speed of 20000rpm to 30000 rpm. In some embodiments, the motor 400 has an idle speed of 5000rpm to 50000 rpm. The motor 400 is rated within 1200W and rated for approximately 45 amps. In some embodiments, the rated power is 600W-1200W; in some embodiments, the power rating is 400W to 1500W; in some embodiments, the power rating is 700W-900W. The motor 400 in some embodiments has an idle speed of 24000rpm and a rated power of 800W, 810W, or 850W.

The motor 400 includes: the motor comprises a motor bearing 50, a motor rotor 51, a motor fan 52, a motor outer cover 54, a motor stator 55, a motor shaft 56, a motor end cover 57 and a connecting bolt 58. The motor end cover 57 is connected to one end of the motor housing 54 through a connecting bolt 58, the motor stator 55 is fixedly installed in the motor housing 54, and the motor rotor 51 is fixed outside the motor shaft 56 in the motor housing 54 to drive the motor shaft 56 to rotate together. The motor bearing 50 is fixed on one end of the motor housing 54 and sleeved outside the motor shaft 56. The motor fan 52 is sleeved outside the motor shaft 56 and rotates along with the motor shaft 56, so as to cool the whole equipment when the air supply machine operates.

The air supply further includes a housing 210. in this embodiment, the motor housing 54 and the motor end cap 57 are considered part of the housing 210. Of course, it will be mentioned later that the housing 210 also includes the clutch housing 34, the reduction mechanism housing 60, and the like. The motor housing 54, the clutch housing 34, and the reduction mechanism housing 60 are fixedly connected. Of course, the case 210 also includes the above-mentioned battery pack mounting portion.

In the present embodiment, it is considered that the brushless and non-inductive high-speed motor has a high rotation speed and a high power, and a cylinder diameter required to be driven is large and an exhaust amount per stroke is large. In this regard, the transmission mechanism includes a reduction mechanism 200. The speed reducing mechanism 200 is used for reducing the speed and increasing the torque, so as to reduce the speed of the high-speed motor 400 and increase the torque to drive the load to operate. Therefore, the weight of the whole air feeder can be reduced, a larger load can be driven, and the requirement of sufficient air displacement in unit time is met. Specifically, the speed reducing mechanism 200 is used for reducing the rotation speed of the output shaft of the motor 400 and driving the piston 1 through the output shaft of the speed reducing mechanism 200. In the present embodiment, the rotation speed of the output shaft of the reduction mechanism 200 is 600rpm or less. Therefore, the air is compressed in the cylinder 4 for a longer time, which is beneficial to heat dissipation and further approaches isothermal compression, the compression efficiency is improved, and the energy loss is small. Specifically, the rotation speed range of the output shaft of the reduction mechanism 200 is 60rpm to 600 rpm. Under the condition that the single stroke displacement of the cylinder 4 is not changed, the rotating speed of the output shaft is smaller than the range, the flow rate of the compression assembly is small, and the working requirement cannot be met; if the rotational speed of the output shaft is greater than this range, the temperature of the cylinder rises, the energy loss is large, and danger is likely to occur.

In some embodiments, the rotation speed ranges from 120rpm to 400 rpm; in some embodiments, the rotation speed ranges from 180rpm to 250 rpm; in some embodiments, the rotation speed ranges from 360rpm to 600 rpm; in some embodiments, the rotation speed ranges from 400rpm to 560 rpm.

Wherein the stroke frequency of the compressing assembly 100 is 60 times per minute to 600 times per minute. Referring to the relationship between the cylinder compression frequency (stroke frequency) and the cylinder exterior temperature shown in fig. 22, it can be seen that the stroke frequency of the compression assembly 100 of the air feeder provided in this embodiment is 60 to 600 per minute, and according to the exterior temperature of the cylinder 4 shown in fig. 22 not exceeding 30 degrees, the heat generated by the cylinder is not significant, and thus the air feeder can be carried around without affecting the user. In some embodiments, the stroke frequency of the compression assembly 100 may be 120 times per minute to 400 times per minute. Further preferably, the stroke frequency may be 180 times per minute to 250 times per minute. In some embodiments, the stroke frequency may be 360 to 600 strokes per minute; in some embodiments, the stroke frequency may be 400 to 560 strokes per minute.

In the present embodiment, the flow rate of the compression assembly 100 may be calculated by multiplying the single stroke displacement of the cylinder 4 by the stroke frequency of the compression assembly 100, and may be calculated according to the following formula: q is V M N. Wherein M is the stroke frequency of the compression assembly 100; n is the number of cylinders. Thus, in some embodiments, the flow rate of the pressure stack assembly 100 is between about 1 liter/s and 2.2 liters/s; in some embodiments, the flow rate of the pressure stack assembly 100 is between about 0.8 liters/s and 2.5 liters/s; in some embodiments, the flow rate of the pack assembly 100 is between about 1.5 liters/s and 2.2 liters/s (i.e., 90 liters/minute to 132 liters/minute); in some embodiments, the flow rate of the pressure stack assembly 100 is between about 1 liter/s and 2 liters/s. May be 1.4 liters/second; 1.8 liters/second, etc.

In the present embodiment, the number of the cylinders 4 is 2, and the rotation speed may be 120rpm to 400 rpm. Of course, in other embodiments, the cylinder 4 may be a single cylinder; the rotation speed may be 400rpm to 560 rpm.

The amount of gas required for each firing of a conventional pneumatic tool, such as a pneumatic nail gun (F30), is 700 ml. In the present embodiment, the air supply amount of the air supply machine is about 1L/s to 2.2L/s, so that the air supply machine can fire the pneumatic nail gun 2 to 3 times per second, thereby satisfying the requirement of continuous operation of the pneumatic tool.

Therefore, in the present embodiment, the stroke frequency (the rotation speed of the output shaft) and the single stroke displacement of the cylinder 4 are preferably designed, wherein the cylinder 4 of the present embodiment has a large diameter and a large stroke, and further the single compressed air volume is large, so that the air supply machine has a high flow rate, and the requirement of the pneumatic tool for continuous operation is met; the reasonable design of stroke frequency (the rotating speed of the output shaft) can not cause the temperature of the cylinder to rise very high, is convenient to carry and avoids energy loss.

In some embodiments, since the battery 600 has a nominal output voltage of about 20V, the gas supply can have a battery voltage ratio Q: V of between about 0.05 liters/s per volt and about 0.11 liters/s per volt. For example, the ratio of flow rate to cell voltage, Q: V, may be about 0.07 liters/s per volt. The high flow rate Q and corresponding flow rate to battery voltage ratio Q: V of the air feeder 10 advantageously allows the air feeder to operate quickly and satisfactorily for pneumatic tools and continue to operate.

In order to provide an air feeder with low energy consumption and large displacement, the ratio of the flow rate of the air feeder to the rated power is optimally designed. The rated power is a power which is consumed in the continuous operation of the air feeder and converted in the air feeder. In some embodiments, the motor 400 has a power rating of up to 1200W, and the result of the optimal ratio of power rating to flow rate for the air feeder is: the battery pack of the air feeder has long power supply time and the discharge capacity is not influenced. Because the air feeder energy consumption is little, improve the duration of battery package, can not reduce the air feed moreover.

The flow rate of the compression assembly 100 is between about 1 liter/s and 2.2 liters/s. Ratio of flow rate of the compression assembly 100 to the rated power for a power range of 1200W, the ratio of the rated power being not less than 1.18cm³and/S/W. If the flow rate of the air feeder is too small in proportion to the rated power, the equivalent power is small and the flow rate is too small to meet the air feeding demand. In some embodiments, the ratio of the flow rate of the compression assembly relative to the rated power is at 1.25cm³(ii)/S/W to 2.75cm³and/S/W. In some embodiments, the ratio of the flow rate of the compression assembly relative to the rated power is at 1.3cm³(ii)/S/W to 2.3cm³and/S/W. Therefore, the air supply machine with low energy consumption and large discharge capacity can be provided without reducing the air supply amount under the condition of improving the cruising ability (low energy consumption) of the battery pack.

Also, the proportion of the single-stroke displacement of the cylinder 4 with respect to the rated power is optimally designed. In some embodiments, the rated power of the motor 400 is within 1200W, and the ratio of the single-stroke displacement of each cylinder 4 to the rated power is 0.12cm³from/W to 0.98cm³W; in some embodiments, the ratio of single-stroke displacement of each cylinder to the rated powerAt 0.18cm³from/W to 0.42cm³/W。

In order to obtain a portable, high-displacement air feeder, the ratio of the weight of the air feeder to the rated power is optimally designed. The weight of the air feeder in the embodiment of the application is less than 6 kilograms for the rated power within 1200W, so that the problem of heavy weight and physical activity of a user carrying the air feeder can be solved. For a rated power of 1200W or less, a ratio of a weight of the air feeder to the rated power is not more than 7.5 g/W. If the weight of the air feeder is too great in proportion to the rated power, the air feeder is cumbersome and inconvenient to carry. As a direct current air supply machine which does not need to be connected with a mains supply, the pneumatic tool is light in weight and good in performance, and is more suitable for being used by a pneumatic tool.

Preferably, the ratio of the weight of the air feeder to the rated power is between 4.38g/W and 7.5 g/W.

Preferably, the ratio of the weight of the air feeder to the rated power is between 3.8g/W and 6.2 g/W. Therefore, the whole machine is lighter in weight and convenient to carry under the condition that the performance of the air feeder is not affected.

Specifically, the weight of the air feeder is less than 6kg for a rated power within 1200W. In some embodiments, the air feeder weighs between 3kg and 5 kg. In some embodiments, the air feeder weighs between 4kg and 5.5 kg.

The weight of the air feeder is the total weight of all components, including the weight of the battery pack 600, which is about 600-800 grams. The weight of the pneumatic tool is not considered, nor is the weight of the connecting air tube for connecting the pneumatic tool.

Wherein the drive assembly comprises a motor and a transmission mechanism. The motor 400 is a brushless non-inductive high-speed motor with high rotation speed and weight of about 500-600 g. The transmission mechanism comprises a speed reducing mechanism and the like, and the weight of the transmission mechanism is about 350-450 g.

The compression assembly 100 comprises a cylinder 4 and a piston 1 which is arranged in the cylinder 4 and is in sliding fit with the cylinder 4, and because the gas is close to isothermal compression, the heat productivity of the cylinder 4 is small, and heat dissipation can be performed without arranging cooling fins; and the cylinder and the piston are made of light and wear-resistant materials, can be made of aluminum or plastic materials, and the whole weight of the compression assembly 100 is 400-550 g.

Because the large-displacement air cylinder is arranged, a large-volume air storage tank is not required, the weight of the whole machine is reduced, the overpressure explosion risk is avoided, and the safety factor is increased.

In order to obtain a portable, large displacement air feeder, the weight to flow rate ratio of the air feeder is also designed in this embodiment so that the air feeder has a high flow rate, is lightweight, and is portable. The ratio of the flow rate of the air feeder to the weight of the air feeder is not less than 0.16 liter/s/Kg. If the flow rate of the air feeder is too small in proportion to the weight of the air feeder, the flow rate is too small for the air feeder of the same weight to meet the air feeding demand. In some embodiments, the ratio of the flow rate of the air feeder relative to the weight of the air feeder ranges from 0.2 liters/s/kg to 0.7 liters/s/kg. In some embodiments, the ratio of the flow rate of the air feeder relative to the weight of the air feeder ranges from 0.25 liters/s/kg to 0.4 liters/s/kg. Of course, the ratio of the flow rate of the air feeder to the weight of the air feeder may be 0.35 liters/s/kg, 0.29 liters/s/kg, and so on.

Thus, the flow rate of the air feeder is optimally designed without increasing the weight. As a direct current air supply machine which does not need to be connected with a mains supply, the direct current air supply machine meets the requirement of continuous work of a pneumatic tool, is light in weight, and is more suitable for being used by the pneumatic tool needing to be replaced in different places. The air feeder can be freely chosen to be carried on the back due to light weight; or hung on the waist; or placed in a convenient location at hand.

In the operation of the gas feeder according to this embodiment, referring to the operation state shown in fig. 20, the gas feeder 2000 is small and light, the operator 1000 can lift the gas feeder 2000 by carrying the gas feeder 2000 with his/her back, and the pneumatic tool (e.g., pneumatic nail gun) 4000 is connected to the quick connector 80 of the gas feeder 2000 through the connecting gas pipe 5000 to supply high-pressure gas. The operator 1000 operates the pneumatic nail gun 4000 to perform a nail-shooting operation on the target work surface 6000.

Different low discharge capacity that generally adopts at present, high rotational speed (high frequency) technique, because adiabatic compression causes the technique cylinder of present day to send out the boiling hot easily, compression efficiency is low, and the frequency of compression risees simultaneously and brings the mechanical wear loss and also increases, so whole compression efficiency receives the influence, makes the effective output gas volume of lithium cell list package reduce. The air feeder of the embodiment adopts a large displacement and low-frequency compression technology which is just opposite to the technology, the air feeder is convenient to carry, the heating of the air cylinder does not influence a user, plug and play can be realized, and the user does not need to wait.

The air feeder further includes a speed reduction mechanism 200 for reducing speed and increasing torque. The speed reducing mechanism 200 is used to reduce the speed of the motor 400 with high rotation speed and increase the torque to drive the load to operate. The power input end of the speed reducing mechanism 200 receives the power of the motor 400 (specifically, the gear 20 is a gear at the output end of the clutch device 300 and is also a gear at the input end of the speed reducing mechanism 200), and the output end of the speed reducing mechanism 200 is connected to the crank 8, so as to drive the piston 1 to make linear reciprocating motion in the cylinder 4. In the present embodiment, the speed reduction mechanism 200 is a three-stage gear reduction, and the total transmission ratio is about 30-150; or 30 to 100; or 50 to 100. In some embodiments, the overall transmission ratio of the speed reducing mechanism is 50-80; of course, the gear ratio may also be 55; 60 or 70, etc. The overall transmission of the reduction mechanism 200 is within a suitable range so that the output shaft to which the high-speed motor is transmitted via the reduction mechanism has an optimum rotational speed. Therefore, the air feeder can have larger displacement and the cylinder can not generate heat due to overhigh frequency.

Specifically, as shown in fig. 9 and 17, the reduction mechanism 200 includes: the reduction mechanism comprises a reduction mechanism shell 60, a primary gear ring 61, a secondary gear ring 62, a secondary planet carrier 64, a bearing 65, a reduction mechanism output shaft 66, a tertiary pin shaft 67, a tertiary gear 68, a secondary pin shaft 69, a secondary gear 70, a primary planet carrier 71, a primary gear 72, a primary pin shaft 73 and a gear 20. The primary pin shafts 73 are pressed into holes in a disc of the primary planet carrier 71 in an interference manner, and a plurality of primary gears 72 are arranged on the primary planet carrier 71 through the primary pin shafts 73; likewise, a secondary gear 70 is disposed on the secondary planet carrier 64 via a secondary pint 69; a tertiary gear 68 is provided on the output shaft 66 through a tertiary pin 67.

The reduction mechanism 200 has, among other things, a gear 20 (described again) at the input end and a reduction mechanism output shaft 66 at the output end. A flange 15 is connected to an end of the reduction mechanism case 60. The reduction mechanism output shaft 66 is rotatably provided in the flange plate 15 around the axis of the output shaft 66, and a bearing 17 and a back-up ring 18 are fitted between the reduction mechanism output shaft 66 and the flange plate 15. In the present embodiment, the axis of the output shaft 66 coincides with the motor axis X of the motor 400. The input gear 20 of the input is driven by the motor shaft 56 of the motor 400. The front end (upper end in fig. 9) of the output shaft 66 of the reduction mechanism 200 at the output end thereof is connected to the crank 8. The reduction mechanism 200 further includes a primary ring gear 61 and a secondary ring gear 62, and the two ring gears of the primary ring gear 61 and the secondary ring gear 62 have different gear modules, wherein the ring gear of the primary ring gear 61 is meshed with the secondary gear 70 and the primary gear 72. The outer surfaces of the ring gears 61, 62 have a plurality of projections in the axial direction, and the sectional shape is a triangle or other geometric shape, and these projections are fitted into the fixed reduction mechanism casing 60.

In power transmission, the power of the gear 20 comes from the motor 400 and corresponds to a primary central wheel. The gear 20 rotates to cause the primary gear 72 to rotate on its own axis, while the primary gear 72 revolves around the axis of the output shaft 66 by causing the primary carrier 71 to revolve. Therefore, a gear (not numbered) on the primary planet carrier 71 is meshed with the secondary gear 70, and the secondary gear 70 is driven to rotate around the axis of the secondary gear 70, and simultaneously the secondary planet carrier 64 is driven to revolve around the axis of the output shaft 66 through the secondary pin 69. In turn, a gear (not numbered) of the secondary planet carrier 64 meshes with the tertiary gear 68, causing the tertiary gear 68 to rotate about its axis and simultaneously causing the output shaft 66 to rotate. Therefore, the power of the reduction mechanism 200 is transmitted to the primary planet carrier 71 through the primary planet gear 72 and the primary pin 73, the protrusion on the primary planet carrier 71 is processed into a sun gear, or a gear is arranged on the protrusion to be used as the sun gear of the next stage, and similarly, the power is finally transmitted to the reduction mechanism output shaft 66 through the secondary gear 70, the secondary pin 69, the secondary planet carrier 64, the tertiary gear 68 and the tertiary pin 67, and the bearing 65 plays a role of supporting the reduction mechanism output shaft 66. Therefore, in the present embodiment, a planetary gear reduction system is adopted, and a large torque can be output with the advantage of small size.

When the compression assembly 100 is loaded and stopped at a random position, the connecting rod crank mechanism may be reversed due to the pressure, and the pressurized high-pressure gas may be changed into low-pressure gas. To avoid wasting the power of the battery pack 600, the air feeder provided in this embodiment is additionally provided with a reverse rotation preventing mechanism. The anti-reverse mechanism causes the output shaft 66 of the reduction mechanism 200 to rotate in one direction. The anti-reverse mechanism includes a one-way clutch provided on the output shaft 66.

In some embodiments, the one-way clutch includes a one-way needle bearing 16, an inner race of the one-way needle bearing 16 is fixedly connected to the output shaft 66, and an outer race of the one-way needle bearing 16 is fixedly connected (interference fit) to the reduction mechanism housing 60. Therefore, the output shaft 66 of the speed reducing mechanism cannot rotate reversely, and the waste of the power of the battery pack 600 is avoided.

As shown in fig. 10 and 11, the cylinder 4 communicates with a buffer tube 82 for storing compressed gas, and a large-sized gas tank is not required. The buffer pipe 82 is disposed on the cylinder 4, and the outer diameter of the buffer pipe 82 is smaller than the inner diameter of the cylinder 4. The capacity of the buffer tube 82 is equivalent to the capacity of the cylinder 4. The length of the buffer tube 82 is below the length of the cylinder 4. The buffer tube 82 has a quick connector 80 thereon to output compressed gas to the pneumatic tool. The buffer pipe 82 is communicated with the cylinder 4, end covers 85 are arranged at two ends of the buffer pipe 82, the end covers 85 are connected with the cylinder 4 through the air outlet pipe 12, two ends of the cylinder 4 are respectively connected with the air outlet pipe 12 through the outlet check valve 11, and backflow of high-pressure gas in the buffer pipe 82 is avoided. The buffer pipe 82 is also provided with a safety valve 83, and when the pressure in the buffer pipe 82 exceeds a certain pressure, the safety valve 83 is automatically opened to release the pressure, so that the safety performance of the equipment is improved. The buffer tube 82 provides a receiving space for a part of the compressed gas and provides a mounting position for a safety valve 83, a quick coupling 80, and a pressure sensor 88 described below.

The air feeder further includes a clutch means 300 for selecting whether to transmit power to the driving assembly through the clutch means during operation of the motor. The clutch device 300 is disposed between the motor 400 and the transmission mechanism, and selectively transmits power of the motor 400 to the driving assembly. That is, the clutch device 300 allows the motor shaft 56 to selectively move the drive assembly. So, the air feeder can be according to pneumatic tool's operating condition, need not to close the motor and just can select to cut off power transmission or switch on power transmission, and can not frequently start the motor to the life of air feeder has been guaranteed.

The clutch device 300 is configured to allow the motor 400 to transmit power when the air pressure (pressure value) of the buffer pipe 82 is lower than a preset pressure, and to cut off the transmission of power of the motor 400 when the air pressure of the buffer pipe 82 is higher than the preset pressure. The clutch device 300 functions to cut off and turn on power, and the cut-off and turn-on are controlled by an actuator (e.g., a pull-up electromagnet 90 described below), and has an input connected to the motor 400 and an output connected to the reduction mechanism 200.

The preset pressure may be a set value or a range value, and in order to avoid frequent starting of the motor 400, the preset pressure is preferably a range value, and the preset pressure may include a preset maximum value and a preset minimum value. Specifically, the clutch device 300 is configured to allow the motor 400 to transmit power when the air pressure (pressure value) of the buffer tube 82 is lower than a preset minimum value, and to cut off the transmission of power of the motor 400 when the air pressure of the buffer tube 82 is higher than a preset maximum value. The preset maximum value can be a pressure value set by a user according to user expectation (for example, rated working air pressure of a target tool), the preset minimum value can have a fixed difference value with the preset maximum value, and then the user does not need to additionally set the preset minimum value after setting the preset maximum value. After so setting, the pressure in the buffer pipe 82 is in the preset pressure (range), that is, when being in the preset highest value and between the preset lowest values, the motor 400 cannot be started in the working state, so that the problem that the motor 400 is frequently started can be avoided, the use noise is reduced, and the use experience of the user is improved.

To facilitate automatic control of the clutch device, the gas supply machine has a controller 500, and a pressure sensor 88 for detecting the value of the gas pressure. The controller 500 is electrically connected to the battery pack 600. The pressure sensor 88 may be provided on the controller 500 or the buffer pipe, and is mainly used to detect the outlet pressure value of the air feeder, that is, the pressure value of the gas discharged from the cylinder 4. The controller 500 is connected to the pressure sensor 88 and the clutch device 300, and controls the on/off of the clutch device 300 according to the detected pressure of the pressure sensor. Specifically, the buffer pipe 82 is provided with a pressure sensor joint 81. The pressure sensor connector 81 is connected with a pressure sensor 88 in the controller through a gas pipe 87. Of course, the pressure sensor 88 may be mounted on the buffer tube 82, and specifically, the pressure sensor 88 may be integrated with the pressure sensor connector 81, and then the lead of the pressure sensor 88 is connected to the controller 500, so that the connection is simple, the processing is convenient, and the cost is low.

The gas supply machine control principle that this application embodiment provided mainly controls clutch 300's separation state according to the change condition of gas pressure to make compression assembly 100 be in work and non-operating condition, stop at non-operating condition at every turn and all be random, it is in the state of calming anger of high pressure load condition to possibly calm anger, if atmospheric pressure does not let out when the second start, motor 400 torsional characteristics is difficult to carry the load restart, at present common practice unload atmospheric pressure earlier through the electromagnetic pneumatic valve before starting and then start, but directly unload atmospheric pressure and can produce very big waste, make the working capacity decline of single battery package calm anger efficiency reduction.

To solve this problem, the air feeder of this embodiment is provided with a flywheel energy storage mechanism (clutch device 300) to avoid the motor 400 from being started with load (starting torque is small). The motor 400 is started and idled at a high speed by the controller 500 before the compression assembly 100 is operated, so that the flywheel 39 coaxial with the motor 400 stores a large part of the rotational kinetic energy when the motor 400 is idled, and at this time, even if the starting clutch device 300 is loaded, the kinetic energy of the flywheel 39 is released to help the motor 400 start with load. This enables the on-load start of the air feeder to be smoothly completed, thereby smoothly solving the problem that the motor 400 cannot be started when the air feeder is on-load.

Specifically, referring to fig. 12 and 13, the clutch device 300 includes a first clutch member 39 supported by the motor shaft, a second clutch member 30 provided with a driving member engaged with the driving assembly, and a moving assembly urging the second clutch member 39 and the first clutch member 30 to be engaged and disengaged. When the second clutch 39 and the first clutch 30 are engaged, it is possible to transmit the power of the motor 400 to the drive assembly (the reduction mechanism 200); when the second clutch 39 and the first clutch 30 are disengaged, the power of the motor 400 cannot be transmitted to the drive assembly (reduction mechanism 200), and the motor 400 idles. In this way, the clutch device can selectively transmit the power of the motor 400 to the driving assembly, that is, selectively transmit the power of the motor 400 to the speed reducing mechanism 200, thereby functioning as a power clutch. In this embodiment, the first clutch member 39 is a flywheel and is fixed to the motor shaft 56 of the motor 400. The flywheel 39 is a part of the clutch device 300, and can be used as an energy storage member when the weight of the flywheel reaches a certain mass, the power of the motor 400 can be stored by the rotational kinetic energy of the flywheel 39, and the kinetic energy of the flywheel 39 can be released to the motor shaft 56 when needed, so that the flywheel and the motor interact with each other, and the effect of reducing the overall vibration is achieved.

The concave surface of the flywheel 39 has a friction bevel 301, i.e. a friction surface, whereby the flywheel 39 is also called a friction disc i. The second clutch member 30, which may also be referred to as a friction disc ii, is movable along the motor axis X to effect engagement and disengagement with the first clutch member 39. The friction surface 301 and the inclined surface of the friction disc II 30 are tightly and seamlessly pressed together to form a pair, and power is transmitted through friction force, so that the power of the motor 400 can be pressed through the two inclined surfaces to transmit the power to the speed reducing mechanism 200, and the effect of power clutch is achieved.

The second clutch 30 is slidably disposed on the motor shaft 56 through the needle bearing 40. The driving member is a gear 20, which can be integrally formed with the second clutch member 30; or may be fixedly connected to the second clutch member 30. Here, the gear 20 is also the input of the reduction mechanism. When the second clutch 39 and the first clutch 30 are engaged, the power of the motor shaft 56 is transmitted to the drive assembly, which also carries the crank 8 via the output shaft 66 of the reduction mechanism 200, thereby causing the piston to reciprocate. When the second clutch 39 is disengaged from the first clutch 30, the power of the motor shaft 56 cannot be transmitted to the driving assembly, and the motor 400 idles to store energy.

The housing 210 includes a clutch housing 34 that houses the clutch device 300. The moving component comprises a static raceway disc 33, a moving raceway disc 32 and raceway steel balls 35 arranged on a clutch housing 34, wherein the moving raceway disc and the static raceway disc are provided with raceways for accommodating the raceway steel balls 35. In order to make the axial movement of the second clutch member 39 relatively smooth, a number of uniformly distributed raceways may be provided. In the present embodiment, the raceways are provided on the facing end surfaces of the stationary raceway disc 33 and the movable raceway disc 32, and 3 raceways are uniformly distributed. In particular, as can be seen in fig. 14a and 14b, the raceways are helical raceways (only the static raceway disc 33 is shown, and the dynamic raceway disc 33 is the same). The raceway steel ball 35 is gradually lifted up in the axial displacement when rolling in the raceway, the raceway is provided with a deep end and a shallow end, the end of the center of the raceway, which is deep (large distance) from the end face, is the deep end, and the end of the center of the raceway, which is shallow (small distance) from the end face, is the shallow end; and smoothly transitions from the deep end to the shallow end. In this way, the axial displacement of the raceway balls 35 as they roll in the raceway is progressive. When the moving race plate 32 rotates, it is axially displaced by the race balls 35 to urge the second clutch member 39 into and out of engagement with the first clutch member 30. The shifting assembly further includes a thrust bearing 38 disposed between the moving race plate 32 and the second clutch member 30. One end of the thrust bearing 38 is abutted against the second clutch member 30 (the friction disc II 30) and can rotate together with the second clutch member 30; one end abuts against the movable raceway plate 32, and is rotatable together with the movable raceway plate 32. And when the moving track disc 32 moves along the motor axis X toward the first clutch member 39, the second clutch member 30 is moved in a direction to engage with the first clutch member 39.

The moving assembly further comprises a solenoid 90 (which is a position attracting electromagnet), an iron core 93 housed within the solenoid, and a connecting member 91 connecting the iron core 93 and the moving race plate 32. In this embodiment, the connecting element 91 is a cable, the movable raceway is provided with a cable connector 92, one end of the cable 91 is connected to the cable connector 92, and the other end is connected to the iron core 93. After the position-absorbing electromagnet 90 is electrified, the iron core 93 is driven to move along the self axial direction, and then the movable rolling way disc 32 is pulled to rotate.

The moving assembly further includes a return mechanism including a return spring 36, the return spring 36 providing a spring force for moving the second clutch member 39 in a direction away from the first clutch member 30. That is, when the piston 1 is not required to be driven to move, the return spring 36 pushes the friction disc ii 30 to be separated from the friction slope of the flywheel 39, and the friction disc ii is in the initial position.

Further, the reset mechanism further includes a limiting member 37, in this embodiment, the limiting member may also be referred to as a steel ball limiting cover 37, the reset spring 36 is disposed between the steel ball limiting cover 37 and the second clutch member 30, and a limiting steel ball 31 is disposed between the steel ball limiting cover 37 and the motor shaft 56. Specifically, the limiting steel ball 31 is arranged in the inner hole of the steel ball limiting cover 37 and is abutted against the motor shaft 56. In this way, the limit steel ball 31 is in point contact with both the ball limit cover 37 and the motor shaft 56, and even if the motor shaft 56 rotates at a high speed, wear can be reduced. One end of the return spring 36 abuts against the bottom of the inner hole of the second clutch member 30, and the other end abuts against the edge of the steel ball limiting cover 37, and the return spring 36 has a certain pre-tightening force after being assembled, that is, when the piston 1 does not need to be driven to move, the return spring 36 pushes the friction disc ii 30 to be separated from the friction inclined plane of the flywheel 39.

As can be seen from the above structural description, the clutch device 300 is mainly divided into 3 functional parts, the first is the combination of the static race plate 33 and the dynamic race plate 32 which generate thrust, the second is the clutch body of the flywheel 39 and the friction plate ii 30, the third is the resetting mechanism of the friction plate ii, fig. 13 is the assembly drawing of the clutch device, and fig. 14 a-16 b are the working principle drawing of the clutch device. The 3 functional sections are described in detail below in order to better understand the present application. The first functional part: the stationary raceway disc 33 and the movable raceway disc 32 are combined. The static raceway disc 33 is tightly attached to the clutch housing 34 in an interference manner, a gap is reserved between the movable raceway disc 32 and the clutch housing 34, and the movable raceway disc 32 can rotate around the axis. Axial power is transmitted between the static raceway 33 and the moving raceway disk 32 through steel balls 35 in the raceways. The moving raceway disc 32 is provided with a boss as a cable connector 92, and the other end of the cable 91 is connected with an iron core 93 of the pull-up electromagnet 90. Because the static raceway disc 33 and the moving raceway disc 32 are both provided with raceways, the deep and shallow ends of the raceways of the static raceway disc 33 and the moving raceway disc 32 correspond to each other during assembly, and in an initial state, i.e., when the attraction electromagnet 90 is not energized, and power is not required to be transmitted to the reduction mechanism 200 by the clutch device 300, the raceway steel balls 35 are positioned at the deep ends of the two raceways, and the distance between the two end faces is the minimum, which is about 7.2 mm as shown in fig. 16 a. When the ball 35 is at the shallow end of the two raceways, the distance between the two end faces is at its maximum of about 9.2 mm, and the difference in distance is 2 mm to 9.2-7.2. This distance difference is also the actuation path of the clutch device. The multiplication of the clutch by the central annular distance (20 mm) between the deep and shallow ends of the raceway divided by this difference and multiplied by 2 is as follows: p ═ 20/2 × (2) ═ 20. It can be seen that the clutch device 300 of the present embodiment has a multiplication effect: the attraction force of the attraction electromagnet 90 is amplified by 20 times. Therefore, the multiplication factor of the clutch device is 20, that is, the force applied to the second clutch member 30 by the cable 91 can be increased by 20 times.

When the pull-up electromagnet 90 is electrified, the iron core 93 pulls the pull rope 91 to drive the movable rolling way disk 32 to rotate, the rolling way steel ball 35 moves from the deep end to the shallow end to drive the movable rolling way disk 32 to move axially, and a larger force can be generated in the axial direction due to multiplication, so that the thrust of the return spring 36 can be overcome to push the friction disk II 30 to move along the axis X direction of the motor, and the friction disk II 30 is in friction joint with the friction disk I to transmit power.

The second functional part: a first clutch member 39 (friction disc I39) and a second clutch member 30 (friction disc II 30) clutch body; according to the principle of friction mechanics, the friction force is in direct proportion to the positive pressure, and the friction force between the friction disc II 30 and the friction disc I is larger, so that the transmission of the power is more beneficial. Thus, the first clutch 39 in this embodiment is provided with a friction ramp to drive the second clutch 30. That is, friction disc II 30 and friction disc I adopt the mode that the friction surface is the inclined plane. As shown in fig. 18, the friction slope has a length h in the axial direction, a radial distance m, a multiplication ratio: p is h/m and P is about 3. Then the multiplication of the entire clutch device 300 is equal to about 20 x 3 ≈ 60. That is, it is more advantageous to transmit the power to amplify the attraction force of the attraction electromagnet 90 by 60 times, that is, to increase the force transmitted by the cable 91 by 60 times until the frictional force acting between the friction disk ii 30 and the friction disk i is increased. In order to increase the friction coefficient and the service life of the friction inclined plane, the friction inclined plane can be embedded with nonmetal wear-resistant materials such as copper.

The third functional part: a resetting mechanism of the friction disc II; the reset mechanism includes: the device comprises a return spring 36, a limiting steel ball 31, a steel ball limiting cover 37, a needle bearing 40, a thrust bearing 38 and a friction disc II 30. One end of the thrust bearing 38 abuts against the friction disc II 30 and rotates together with the friction disc I (flywheel 39), and the other end abuts against the moving raceway disc 32 and rotates together with the moving raceway disc 32. The reset spring 36, the spacing steel ball 31, the spacing cover 37 of steel ball is built-in friction disc II 30, and reset spring 36 one end offsets in friction disc II 30 hole bottom, and one end offsets in the spacing cover 37 platform edges of steel ball, and spacing steel ball 31 is built-in the spacing cover 37 hole of steel ball, and there is certain pretightning force in reset spring 36 after the assembly for reset spring 36 promotes friction disc II 30 and breaks away from the friction inclined plane.

The working process of the resetting mechanism is as follows: when the pull-in electromagnet 90 is electrified, the iron core 63 is stressed to pull the dynamic rolling disc 32 to rotate through the pull rope 91, and due to the multiplication relation, a larger force is generated in the axial direction, and the larger force overcomes the thrust of the return spring 36 to push the friction disc II 30 to move in the axial motor direction, so that the friction disc II 30 is in friction contact with the friction disc I to transmit power. When the attraction electromagnet 90 is powered off, the friction disc II 30 is separated from the friction disc I in friction contact under the action of the return spring 36, and power transmission is released. The power-on and the power-on time of the pull-up electromagnet 90 are controlled by a controller 500 (MCU).

The operation of the air feeder of the present embodiment will be described in detail below with reference to the control flow chart of the air feeder provided in fig. 21 for a better understanding of the present application.

The power switch of the air feeder is turned on and the battery pack 600 supplies power to the respective components. The pull-up electromagnet 90 is controlled to be de-energized to ensure that the clutch device 300 is in the disengaged state, and the current state of the gas feeder is set to the initial state. The starter motor 400 is idle.

The controller 500 then receives a sensed pressure signal from the pressure sensor 88 on the buffer tube 82. The outlet pressure value of the air feeder from the pressure signal is compared with a preset pressure value, and the controller 500 controls the clutch device to be in the disengaged state when the detected pressure value of the pressure sensor 88 is above a preset maximum value. Because the pressure in the buffer tube 82 is over high when the detected pressure value of the pressure sensor 88 is above the preset maximum value, the controller 500 controls the pull-up electromagnet 90 to be powered off, the first clutch member and the second clutch member are separated under the action of the reset mechanism, that is, the friction disc ii 30 is separated from the friction disc i 39, the clutch device 300 does not transmit the power of the motor 400 to the driving assembly, that is, the clutch device 300 cuts off the power transmission of the motor 400, and at this time, the motor 400 is controlled to idle for more than a preset time (in this embodiment, the motor continues to idle for more than 10 seconds), and then the motor is turned off. When the pressure value is lower than the preset minimum value, and when the detected pressure value of the pressure sensor 88 is lower than the preset maximum value, the controller 500 continuously judges whether the detected pressure value is lower than the preset minimum value. When the detected pressure value of the pressure sensor 88 is lower than or equal to the preset minimum value, the controller 500 controls the clutch device 300 to be in the engaged state. The initial state of the air feeder is corrected to an operating state. It is determined whether the motor 400 is in the activated state.

When the motor 400 is not started, it is determined whether the clutch device 300 is in the disengaged state (whether the friction disc ii 30 is disengaged from or in contact with the friction disc i 39, specifically, the disengaged state of the clutch device 300 may be determined by the energized state of the attraction electromagnet 90). When the clutch device 300 is not in a separation state, the attraction electromagnet 90 is powered off, the motor 400 is started, then the attraction electromagnet 90 is switched on, the friction disc II 30 is engaged with the friction disc I39, the clutch device 300 transmits the power of the motor 400 to the driving assembly (the speed reducing mechanism 200), and therefore the piston 1 is enabled to reciprocate to compress air, and the motor 400 is stopped until the pressure value is larger than the preset maximum value.

When the motor 400 is started, the pull-up electromagnet 90 is turned on, and the clutch device 300 is driven to compress air.

And when the detected pressure value is smaller than the preset highest value but larger than the preset lowest value, determining whether the current state of the air feeder is an initial state or a working state, and when the current state is determined to be the initial state, circularly judging whether the pressure value is larger than the preset highest value until the pressure value is below the preset lowest value, wherein air compression is not performed in the process. And when the working state is determined, entering a step of judging whether the motor is started or not until the motor 400 is started to enable the pressure value to exceed a preset maximum value, and then closing the motor 400.

As described above, the gas supplier according to the present embodiment controls the separation state of the clutch device 300 according to the pressure change of the compressed gas of the gas supplier, so that it is possible to intelligently control whether the compression assembly 100 is operated or not operated, and thus, it is possible to realize plug and play and supply gas as needed without providing a gas tank.

Any numerical value recited herein includes all values from the lower value to the upper value that are incremented by one unit, provided that there is a separation of at least two units between any lower value and any higher value. For example, if it is stated that the number of a component or a value of a process variable (e.g., temperature, pressure, time, etc.) is from 1 to 90, preferably from 20 to 80, and more preferably from 30 to 70, it is intended that equivalents such as 15 to 85, 22 to 68, 43 to 51, 30 to 32 are also expressly enumerated in this specification. For values less than 1, one unit is suitably considered to be 0.0001, 0.001, 0.01, 0.1. These are only examples of what is intended to be explicitly recited, and all possible combinations of numerical values between the lowest value and the highest value that are explicitly recited in the specification in a similar manner are to be considered. Unless otherwise indicated, all ranges include the endpoints and all numbers between the endpoints. The use of "about" or "approximately" with a range applies to both endpoints of the range. Thus, "about 20 to about 30" is intended to cover "about 20 to about 30", including at least the endpoints specified.

All articles and references disclosed, including patent applications and publications, are hereby incorporated by reference for all purposes. The term "consisting essentially of …" describing a combination shall include the identified element, ingredient, component or step as well as other elements, ingredients, components or steps that do not materially affect the basic novel characteristics of the combination. The use of the terms "comprising" or "including" to describe combinations of elements, components, or steps herein also contemplates embodiments that consist essentially of such elements, components, or steps.

A plurality of elements, components or steps can be provided by a single integrated element, component or step. Alternatively, a single integrated element, component or step may be divided into separate plural elements, components or steps. The disclosure of "a" or "an" to describe an element, component or step is not intended to exclude other elements, components or steps.

It is to be understood that the above description is intended to be illustrative, and not restrictive. Many embodiments and many applications other than the examples provided will be apparent to those of skill in the art upon reading the above description. The scope of the present teachings should, therefore, be determined not with reference to the above description, but should instead be determined with reference to the appended claims, along with the full scope of equivalents to which such claims are entitled. The disclosures of all articles and references, including patent applications and publications, are hereby incorporated by reference for all purposes. The omission in the foregoing claims of any aspect of the subject matter that is disclosed herein is not intended to forego such subject matter, nor should it be construed that the utility model does not contemplate that such subject matter is part of the disclosed utility model subject matter.

Claims

1. An air feeder, characterized in that: the air feeder includes:

a housing;

a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis;

a battery pack connected to the case;

a compression assembly including a cylinder and a piston disposed within the cylinder;

the driving assembly is used for converting the rotating motion of the motor shaft into the reciprocating motion of the piston in the cylinder and comprises a speed reducing mechanism, and the speed reducing mechanism is used for reducing the rotating speed of the motor shaft and driving the piston to reciprocate through an output shaft of the speed reducing mechanism; the inner diameter of the cylinder is 50 mm to 100 mm, and the stroke of the piston is 40 mm to 100 mm; the rotating speed range of the output shaft is 60 rpm-600 rpm.

2. The air feeder of claim 1, wherein: the rotating speed range of the output shaft is 120 rpm-400 rpm.

3. The air feeder of claim 1, wherein: the rotating speed range of the output shaft is 360-600 rpm.

4. The air feeder of claim 1, wherein: the cylinder has an inner diameter in the range of 50 mm to 80 mm.

5. The air feeder of claim 1, wherein: the piston stroke is 40 mm to 70 mm.

6. The air feeder of claim 1, wherein: the speed reducing mechanism is used for reducing speed through three stages of gears, and the total transmission ratio is 50-80.

7. The air feeder of claim 1, wherein: the rated power of the motor is 600W-1200W.

8. The air feeder of claim 1, wherein: the idling speed of the motor is 18000-30000 rpm.

9. The air feeder of claim 1, wherein: the flow rate of the compression assembly is between 1 liter/s and 2.2 liters/s.

10. An air feeder, characterized in that: the air feeder includes:

a housing;

a battery pack connected to the case;

a motor located within the housing, the motor defining a motor axis and including a motor shaft rotatable about the motor axis,

a compression assembly including a cylinder and a piston disposed within the cylinder; a drive assembly for converting rotational motion of the motor shaft to reciprocating motion of the piston within the cylinder;

the rated power of the motor is within 1200W; the ratio of the flow rate of the compression assembly to the rated power is not less than 1.18cm³/S/W。

11. The air feeder of claim 10, wherein: the ratio of the flow rate of the compression assembly to the rated power is at 1.25cm³(ii)/S/W to 2.75cm³/S/W。

12. The air feeder of claim 10, wherein: the ratio of the flow rate of the compression assembly to the rated power is at 1.3cm³(ii)/S/W to 2.3cm³/S/W。