CN204533762U - Speed reducing mechanism and electronic expansion valve comprising same - Google Patents
Speed reducing mechanism and electronic expansion valve comprising same Download PDFInfo
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- CN204533762U CN204533762U CN201520012787.3U CN201520012787U CN204533762U CN 204533762 U CN204533762 U CN 204533762U CN 201520012787 U CN201520012787 U CN 201520012787U CN 204533762 U CN204533762 U CN 204533762U
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- reducing gear
- side limit
- limit component
- reducing
- output shaft
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Abstract
The utility model relates to a reduction gears and including this reduction gears electronic expansion valve. According to one aspect, there is provided a speed reducing mechanism (80, 80A) including: a speed reduction mechanism housing (82, 82A); a reduction gear train provided in the reduction mechanism housing; an output shaft (88, 88A) connected to the reduction gear train; and an axial limit mechanism (LM, LMA) provided in the speed reduction mechanism. The axial stopper mechanism includes an axial side stopper member (882, 91, 886A, 95A) integrally formed with or fixedly attached to the output shaft and a housing side stopper member (825, 97A) integrally formed with or fixedly attached to the speed reduction mechanism housing, the axial side stopper member and the housing side stopper member being adapted to cooperate with each other to restrict axial displacement of the output shaft. According to the utility model discloses, thereby can eliminate or reduce the axial float of reduction gears's output reliably and avoid the gear pair among the reduction gears to directly bear big axial load.
Description
Technical field
The utility model relates to reducing gear and comprises the electric expansion valve of this reducing gear, more specifically, relates to and in the axial limiting of reducing gear, to have the reducing gear of improvements and comprise the electric expansion valve of this reducing gear.
Background technique
Electric expansion valve is the vitals in cooling/heating system, is mainly used in regulating the flow of working fluid (refrigerant fluid).Conventional electric expansion valve generally adopts stepper motor to control, and is usually made up of driving mechanism (stepper motor), actuator (thread screw mechanism), throttle mechanism (needle valve seat) and relevant assisting agency.
When electric expansion valve is applied to the large system of refrigerating capacity, cause because required refrigerating capacity increases valve opening size to increase and then cause valve assembly can bear the large pressure caused by pressure reduction between hyperbaric chamber and low-pressure cavity when switch valve, therefore time switch valve (such as opening valve), needing the power overcome to increase thereupon.In this case, the reducing gear adopting the such as fixed shaft gear train reducing gear being connected in motor downstream and so on is proposed, to be increased by input torque and the moment of torsion of increase to be exported to the corresponding screw-driven component being connected in reducing gear downstream.
But, in the electric expansion valve adopting fixed shaft gear train reducing gear, space (especially radial space) shared by fixed shaft gear train reducing gear is comparatively large and cause the size of electric expansion valve to increase, and the reduction speed ratio (velocity ratio) that can obtain when same volume/size is also less.In addition, in the electric expansion valve adopting such as fixed shaft gear train reducing gear, shortage reliably can be born larger axis and causes to the structure of load the gear pair in reducing gear directly to bear large thrust load and cause gear pair to be easy to damage, and, be also easy to cause the output terminal of reducing gear and the corresponding screw-driven component that connects with it produce large axial float and cause guaranteeing the accurate valve switch of electric expansion valve.
Therefore, in the art, for the electric expansion valve applied in large cooling capacity systems, there is selecting and space that the axial limiting aspect of reducing gear is improved and demand reducing gear.
Here, it is pointed out that the technology contents provided in this part is intended to contribute to those skilled in the art to understanding of the present utility model, and not necessarily form prior art.
Model utility content
Total summary of the present utility model is provided in this part, instead of the complete scope of the utility model or the utility model institute characteristic comprehensively open.
An object of the present utility model is to provide a kind of reducing gear as described below and a kind of electric expansion valve comprising this reducing gear, can eliminate or reduce the large axial clearance of its output terminal thus can large axial float occur to guarantee the accurate valve switch of electric expansion valve by the associated components eliminated or reduce when electric expansion valve operates in actuator in this reducing gear.
Another object of the present utility model is to provide a kind of reducing gear as described below and a kind of electric expansion valve comprising this reducing gear, the gear pair in reducing gear can be avoided directly to bear large thrust load and cause gear pair to be easy to damage in this reducing gear.
Another object of the present utility model is to provide a kind of reducing gear as described below and a kind of electric expansion valve comprising this reducing gear, by this reducing gear, make electric expansion valve can be adapted to large cooling capacity systems well and without the need to adopting output torque very large thus cost is very high and the motor that size is very too fat to move.
Another object of the present utility model is to provide a kind of reducing gear as described below and a kind of electric expansion valve comprising this reducing gear, owing to adopting planetary gear reducing mechanism as this reducing gear, shared space is less and be easy to construct compact electronic expansion valve, and the reduction speed ratio that can obtain when same volume/size is also larger.
One or more to achieve these goals, according to an aspect of the present utility model, provide a kind of reducing gear, comprising: reducing gear housing; Be arranged on the reducing gear train in described reducing gear housing; The output shaft be connected with described reducing gear train; And the axial limiting mechanism be arranged in described reducing gear.Described axial limiting mechanism comprises the axle side limit component being integrally formed in or being fixedly connected to described output shaft and the case side limit component being integrally formed in or being fixedly connected to described reducing gear housing, and described axle side limit component and described case side limit component are suitable for the axial displacement cooperatively interacting to limit described output shaft.
According in reducing gear of the present utility model, described reducing gear train is configured to planetary gear reducing mechanism.
According in reducing gear of the present utility model, described reducing gear housing teeth portion in roughly tubular and in the gear ring that the inner circle wall place of described reducing gear housing is formed as described planetary gear reducing mechanism.
According in reducing gear of the present utility model, described reducing gear train comprises sun gear and planet wheel, external impetus inputs to described sun gear, and a part for described output shaft is configured to planet carrier and operatively connects to export the moment of torsion increased because of deceleration with described planet wheel.
According in reducing gear of the present utility model, engagement portion is formed at the inner circle wall place of described reducing gear housing, described engagement portion is suitable for tightening together with fastening piece, and described fastening piece is suitable for keeping described planet wheel and/or described sun gear together with described output shaft.
According in reducing gear of the present utility model, described fastening piece is threaded connection and is fastened to described engagement portion with axial adjustable way.
According in reducing gear of the present utility model, described axial limiting mechanism also comprises thrust bearing.
According in reducing gear of the present utility model, described thrust bearing is be arranged on the unilateral thrust rolling bearing between described axle side limit component and described case side limit component.
According in reducing gear of the present utility model, described axle side limit component comprises the first axle side limit component and the second axle side limit component, described output shaft comprises head, intermediate portion and terminal part, the stepped part as described first axle side limit component is formed between described head and described intermediate portion, be fastened with the fitting as described second axle side limit component at described terminal part place, and be formed with the lip part be placed between described stepped part and described fitting as described case side limit component at the inner circle wall place of described reducing gear housing.
According in reducing gear of the present utility model, described unilateral thrust rolling bearing comprises the first unilateral thrust rolling bearing be arranged between described stepped part and described lip part and the second unilateral thrust rolling bearing be arranged between described lip part and described fitting.
According in reducing gear of the present utility model, described fitting is threaded connection and is fastened to described terminal part with axial adjustable way.
According in reducing gear of the present utility model, also comprise the fastening screw trip bolt for described fitting being fastened to further described terminal part.
According in reducing gear of the present utility model, described thrust bearing is bidirectional propulsion rolling bearing.
According in reducing gear of the present utility model, described axle side limit component comprises the first axle side limit component and the second axle side limit component, and described case side limit component comprises the first case side limit component and the second case side limit component, described output shaft comprises head, intermediate portion and terminal part, the stepped part as described first axle side limit component is formed at described intermediate portion place, the anchor log as described second axle side limit component is fastened with at described terminal part place, and the lip part be formed at the inner circle wall place of described reducing gear housing as described first case side limit component, and the bounding means be fastened with at the inner circle wall place of described reducing gear housing as described second case side limit component.
According in reducing gear of the present utility model, described bidirectional propulsion rolling bearing is arranged between described lip part and described bounding means, and the middle blowout patche that is positioned at of described bidirectional propulsion rolling bearing is compared more outstanding towards radially inner side with first seat ring being positioned at two ends of described bidirectional propulsion rolling bearing with the second seat ring, make described blowout patche be suitable for being clipped in the middle by described stepped part and described anchor log.
According in reducing gear of the present utility model, described anchor log is threaded connection and is fastened to described terminal part with axial adjustable way, and/or described bounding means is threaded connection the inner circle wall being fastened to described reducing gear housing with axial adjustable way.
According in reducing gear of the present utility model, described axial limiting mechanism also comprises thrust slide bearing.
According in reducing gear of the present utility model, described axle side limit component and described case side limit component in the following way in one or more modes realize being slidably matched: a) between described axle side limit component and described case side limit component, be provided with the wear-resistant pad with self-lubricating function, the surface of at least one b) in described axle side limit component and described case side limit component is coated with the wear-resistant material layer with self-lubricating function, and c) charging-up lubricant oil fat between described axle side limit component and described case side limit component.
One or more to achieve these goals, according to another aspect of the present utility model, provide a kind of electric expansion valve, comprising: frame set; Valve assembly, described valve assembly comprises movable valve member and for regulating the flow of the fluid flowing through described electric expansion valve; Actuator, described actuator carries out axial motion for driving described movable valve member; And driving mechanism, described driving mechanism is used for providing power to described actuator.Described actuator comprises reducing gear as above, and described actuator drives described movable valve member to carry out axial motion via the output shaft of described reducing gear.
According in electric expansion valve of the present utility model, described reducing gear housing forms the integral part of described frame set.
According in electric expansion valve of the present utility model, also comprise the sleeve of the part forming described frame set, wherein, described reducing gear housing is contained in described sleeve together with the rotor of described driving mechanism, and described reducing gear housing is fixedly connected to described sleeve.
According in electric expansion valve of the present utility model, the outside of described reducing gear housing be exposed to external environment condition and with form described frame set a part other component in counterpart member be connected.
According to the utility model, due to adopt in the output terminal of reducing gear so-called can not manual teardown formula (axis) location/limit structure, especially adopting (axis) location/limit structure of form integratedly, there is large axial float thus cannot guarantee the situation of the accurate valve switch of electric expansion valve in the associated components (output shaft and the anti-rotational latch engaged of reducing gear) can eliminated when axial clearance is large, electric expansion valve operates in actuator.And, the large thrust load (stretch and/or compression) that reducing gear bears when operating such as all or part ofly via thrust-bearing can be offloaded on lip part and to be passed on housing further, thus avoids the gear pair in reducing gear (sun gear and planet wheel, planet wheel and interior teeth portion) directly bear large thrust load and cause gear pair to be easy to damage.
On the other hand, according to the utility model, owing to have employed reducing gear (especially planetary gear reducing mechanism), make electric expansion valve can be adapted to large cooling capacity systems well and without the need to adopting output torque very large thus cost is very high and the motor that size (especially the size of stator) is very too fat to move.In addition, when using planetary gear reducing mechanism, shared space (especially radial space) is less and be easy to construct compact electronic expansion valve, and the reduction speed ratio (velocity ratio) that can obtain when same volume/size is also larger.
Accompanying drawing explanation
By the description referring to accompanying drawing, the feature and advantage of one or more mode of execution of the present utility model will become easier to understand, in the accompanying drawings:
Fig. 1 is the longitudinal sectional view of the electric expansion valve illustrated according to the utility model first mode of execution;
Fig. 2 A and Fig. 2 B illustrates according to the three-dimensional longitudinal section of the exploded perspective view Sum decomposition of the electric expansion valve of the utility model first mode of execution;
Fig. 3 A and Fig. 3 B is the three-dimensional longitudinal section of exploded perspective view Sum decomposition of the reducing gear of the electric expansion valve illustrated according to the utility model first mode of execution respectively; And
Fig. 4 A, Fig. 4 B and Fig. 4 C are the exploded perspective view of a part for the reducing gear of the electric expansion valve illustrated according to the utility model second mode of execution, exploded perspective longitudinal section and assembled state longitudinal section respectively.
Embodiment
With reference to the accompanying drawings, by illustrative embodiments, the utility model is described in detail.Be only for purpose of explanation to following detailed description of the present utility model, and be never the restriction to the utility model and application or purposes.
Fig. 1 is the longitudinal sectional view of the electric expansion valve illustrated according to the utility model first mode of execution.Below, with reference to Fig. 1, the general structure according to the electric expansion valve 1 of the utility model first mode of execution is described.
Electric expansion valve 1 according to the utility model first mode of execution can comprise: for the valve assembly 10 regulated the flow of the fluid flowing through electric expansion valve 1; For the actuator 50 driving the movable valve member (i.e. needle) of valve assembly 10 to carry out axial motion; And provide the driving mechanism 40 of power for actuator 50.
Valve assembly 10 can comprise valve body 12.The entrance 12-1 be connected with inflow pipe IT and the outlet 12-2 be connected with outflow tube OT is provided with in valve body 12.Fluid flows into electric expansion valve 1 via inflow pipe IT, then flows out electric expansion valve 1 via outflow tube OT.
In some instances, standing valve component (i.e. valve seat) 18 is set at the outlet 12-2 place of valve body 12.
As mentioned above, the valve assembly 10 of electric expansion valve 1 can also comprise needle (movable valve member) 14.And as mentioned above, needle 14 carries out axial motion under the drive of actuator 50, thus valve seat 18 can be departed from and open electric expansion valve 1 and engage with valve seat 18 and close electric expansion valve 1 and the valve opening of electric expansion valve 1 can be regulated.Needle 14 can comprise first end (upper end) 14-1 and the second end (lower end) 14-2.First end 14-1 is used for and is hereafter engaged by the lower curtate (needle joining portion) of the anti-rotational latch be described further.Second end 14-2 is used for engaging with valve seat 18 thus closing the valve opening at valve seat 18 place.
In the example shown in the series of figures, driving mechanism 40 can be the motor (such as stepper motor) 40 comprising stator 41 and rotor 42.Rotor 42 can sideway swivel in stator 41.In addition, sleeve 44 can be set between stator 41 and rotor 42 to realize the object of easy to assembly and easy sealing.Sleeve 44 in roughly cylindric, and can form a part of the frame set CA of electric expansion valve 1.Here it should be noted that, in this application, frame set CA can comprise any actionless parts in electric expansion valve.
In some instances, rotor 42 can form as one (such as integrally molded) with the axle 51 of actuator 50, and the rotor 42 when driving mechanism (motor) 40 is energized can be rotated integratedly with axle 51.In other example, rotor 42 can be individually formed with axle 51 and then together with being permanently connected by appropriate ways.
Actuator 50 can comprise: axle 51 as mentioned above; Lower support element 53; Anti-rotational latch 55; And reducing gear 80.
In some instances, axle 51 can comprise first end (upper end) 51-1 and the second end (lower end) 51-2.First end 51-1 is used for rotatably engaging with lid component 70 (forming a part of the frame set CA of electric expansion valve 1) (bearing 75---such as sliding bearing 75---such as via the recess being arranged in lid component 70 realizes engaging).Second end 51-2 is used for and is hereafter engaged (such as key is connected) by the sun gear of the reducing gear 80 be described further, and sun gear can be rotated integratedly with axle 51.
In the example shown in the series of figures, lower support element 53 can roughly tubular in hollow and be suitable for being fixedly attached to hereafter by the reducing gear housing of reducing gear 80 that is described further.In some instances, a part (top) for lower support element 53 is press-fitted in reducing gear housing by interference fit.Lower support element 53 can comprise anti-rotation portion 53-2.Anti-rotation portion 53-2 may be embodied as non-circular or polygonal through hole, but this through hole, for holding the upper curtate of anti-rotational latch 55 hereafter will be described further, makes the upper curtate of anti-rotational latch 55 can carry out axial motion can not be rotated around its axis in the anti-rotation portion 53-2 of lower support element 53.
In the example shown in the series of figures, anti-rotational latch 55 can comprise: upper curtate (internal thread part) 55-1; And lower curtate (needle joining portion) 55-2.Can hole be formed in upper curtate 55-1---such as through hole, this hole can have round-shaped, and can be formed with internal thread in this hole.Thus, the upper curtate 55-1 of anti-rotational latch 55 is by its internal thread and be hereafter threadedly engaged by the output shaft of the reducing gear 80 be described further, thus force anti-rotational latch 55 together with needle 14 to carry out axial motion by the rotation of output shaft at output shaft axial restraint under the fixing state of anti-rotational latch 55 circumference, realizing the opening of electric expansion valve 1, close and the adjustment of valve opening.In addition, the upper curtate 55-1 of anti-rotational latch 55 can have the non-circular or polygonal outer periphery matched with the non-circular or polygonal inner circumferential of the through hole of the anti-rotation portion 53-2 of lower support element 53.Thus, non-circular or polygonal outer periphery by the non-circular or polygonal inner circumferential structure of the through hole of the anti-rotation portion 53-2 of lower support element 53 and the upper curtate 55-1 of anti-rotational latch 55 constructs, and anti-rotational latch 55 can not be rotated together with the needle 14 engaged with anti-rotational latch 55 can only carry out axial translational movement relative to lower support element 53.
The lower curtate 55-2 of anti-rotational latch 55 is used for engaging with the first end 14-1 of needle 14 (such as realizing engaging by back-up ring 19).In some instances, needle 14 can be engaged in the second section 55-2 of anti-rotational latch 55 regularly.In other example, needle 14 can be engaged in the lower curtate 55-2 of anti-rotational latch 55 with being axially moveable.In this case, Compress Spring 38 can be set.When moving down when anti-rotational latch 55 and abut with valve seat 18 when needle 14; it is suitable for power to make to have between needle 14 and valve seat 18 that Compress Spring 38 applies spring force from the first end 14-1 of needle 14; thus protect because having contact buffering on the one hand needle 14 and valve seat 18 not damaged, then provide reliable sealing effect on the other hand.
With further reference to Fig. 2 A, Fig. 2 B, Fig. 3 A and Fig. 3 B, (Fig. 2 A and Fig. 2 B illustrates according to the three-dimensional longitudinal section of the exploded perspective view Sum decomposition of the electric expansion valve of the utility model first mode of execution, and Fig. 3 A and Fig. 3 B is the three-dimensional longitudinal section of exploded perspective view Sum decomposition of the reducing gear of the electric expansion valve illustrated according to the utility model first mode of execution respectively), reducing gear 80 may be embodied as epicyclic reduction mechanism 80---be specially planetary gear reducing mechanism 80.Thus, in the application scenarios of large cooling capacity systems, enough decelerations can be provided thus enough output torques are provided, can avoid directly utilizing stepper motor to drive thread screw mechanism to cause needing to adopt output torque very large to realize valve operation thus cost is very high and the motor that size (especially the size of stator) is very too fat to move simultaneously.In addition, compared with adopting the situation of fixed shaft gear train, shared space (especially radial space) is less and be easy to construct compact electronic expansion valve, and the reduction speed ratio (velocity ratio) that can obtain when same volume/size is also larger.
In the example shown in the series of figures, reducing gear 80 can comprise: reducing gear housing 82; Sun gear 84; Planet wheel 86; And output shaft (output terminal) 88 (in present specification, the structure element realizing deceleration and transmission of power by engaging in reducing gear 80 can be called reducing gear train).
Reducing gear housing 82 can be the roughly tubular of hollow.Reducing gear housing 82 can form a part of the frame set CA of electric expansion valve 1.In some instances, when arranging sleeve 44, reducing gear housing 82 can be contained in sleeve 44 together with the rotor 42 of motor 40, is beneficial to assembling and the sealing of electric expansion valve 1.Here, reducing gear housing 82 can be press-fitted in sleeve 44 by interference fit, thus is fixedly connected to sleeve 44 and is positioned at below rotor 42 in sleeve 44.In other example, when not arranging sleeve 44 or set sleeve 44 only for encapsulating rotor 42, reducing gear housing 82 can be exposed to external environment condition and can be connected with other the corresponding component in frame set CA by suitable connector element and/or sealing component.
As shown in Figure 1, reducing gear housing 82 can comprise from top to bottom: engagement portion 821; Interior teeth portion 823; Lip part 825 (being used as according to case side limit component of the present utility model); And auxiliary section 827.
Engagement portion 821 may be embodied as screw threads for fastening portion and is suitable for and is provided with externally threaded fastening piece FP and is threaded (being permanently connected), so that up to hereafter the planet wheel be described further being carried out axially locating/spacing.Fastening piece FP can be provided with central through bore and pass for the second end 51-2 of axle 51, and the second end 51-2 can be engaged with the center hole of sun gear 84.Here, it is pointed out that the above-mentioned screw thread that is fixedly not limited between engagement portion 821 and fastening piece FP is fixed.
Interior teeth portion 823 is equivalent to the gear ring (ring gear) in typical planetary gear reducing mechanism.Interior teeth portion 823 is suitable for engaging with planet wheel 86.Here, because the ring gear (interior teeth portion 823) for engaging with planet wheel 86 is formed directly into a part for the inner circumferential of reducing gear housing 82, therefore can simplified structure thus be reduced to principal and interest in assembling.
Lip part 825 roughly radially inwardly can extend from the inner circle wall of reducing gear housing 82 and can be formed as complete (continuously) annular.But in other example, lip part 825 can be formed as the discontinuous annular lip part (not shown) be made up of multiple discrete lobes.
On the other hand, in some instances, lip part 825 can form with the remaining part of reducing gear housing 82 (body of reducing gear housing) (such as by comprising the molded mode of injection moulding, forging type), to make lip part 825 more stably and reliably can play the axial limiting effect of the output terminal (output shaft) to reducing gear.In other example, lip part 825 can be individually formed and then be fixedly connected to the inner circle wall of the body of reducing gear housing 82 by appropriate ways (such as weld, bond or screw thread is fixedly connected with).Owing to being formed with the lip part 825 for carrying out axial limiting (unidirectional or bi-directional axial is spacing) to the output shaft of reducing gear 80 of the body that forms or be individually formed and then be fixedly connected to reducing gear housing 82 with the body of reducing gear housing 82, back-up ring is adopted with correlation technique, the structures such as the jump ring position structure of manual teardown (can) are compared the scheme that the output terminal of reducing gear carries out axial limiting, axial clearance can be eliminated large, there is the situation of large axial float in the associated components (output shaft and the anti-rotational latch engaged of reducing gear) during electric expansion valve operation in actuator.
Here, it is to be noted, in present specification, also statement " can manual teardown " can be adopted to represent when usually usually not having flexible location/limit structure (such as back-up ring by what can free-handly carry out when external tool mounting and dismounting, jump ring etc.), and also can adopt statement " can not manual teardown " represent usually needs can be formed by external tool/device or carry out installing and/or can dismantle or destroy usually not there is flexible location/limit structure (such as, form or be individually formed and then pass through such as to weld, location/limit structure that the modes such as bonding or screw thread are fixedly connected with are permanently connected together).
Auxiliary section 827 such as can hold entirety or its part (top) of lower support element 53 by interference fit.
Because the structure such as lip part 825 playing teeth portion in decelerating effect 823 and play axial limiting effect is all formed/be arranged in single component (i.e. reducing gear housing 82), therefore can simplified structure, reduction cost, be beneficial to and assemble and guarantee the quiet run of reducing gear and then whole actuator.
In the example shown in the series of figures, single sun gear 84 (special in Fig. 3 A and Fig. 3 B) is set.Sun gear 84 is suitable for engaging with the second end 51-2 of axle 51.Particularly, the center hole of sun gear 84 is suitable for such as being engaged by key Placement with the second end 51-2 of axle 51, and sun gear can be rotated along with the rotation of axle 51.
In the example shown in the series of figures, three planet wheels 86 (special in Fig. 3 A and Fig. 3 B) are set.Planet wheel 86 is arranged around sun gear 84 and is placed in radial directions in sun gear 84 and reducing gear housing 82 between teeth portion 823, thus engages with both planet wheel 86 and interior teeth portion 823.Can be provided with center hole 861 in planet wheel 86, center hole 861 is for holding corresponding pin 89, and this respect will be described further hereinafter.Here, it is pointed out that and also can arrange more than three or be less than the planet wheel of three.
In the example shown in the series of figures (special in Fig. 3 A and Fig. 3 B), output shaft 88 (part for output shaft 88 can be considered as being equivalent to the planet carrier in typical planetary gear reducing mechanism) can comprise from top to bottom: head 881; Intermediate portion 883; And fastening end (also claiming screw-driven portion or terminal part) 887.The portion of topping bar 882 (being used as according to axle side limit component of the present utility model or the first axle side limit component) can be formed between head 881 and intermediate portion 883, and stepped down part 884 can be formed with between intermediate portion 883 and fastening end 887.
In the example shown in the series of figures, circular groove 881a can be formed with in the upper surface of head 881.Groove 881a is suitable for holding the bottom of sun gear 84, is beneficial to the centering of sun gear 84 thus and can guides the rotation of sun gear 84.But, in other example, the groove at the upper surface place of lip part can be omitted.In this case, the lower surface of sun gear 84 can contact with the upper surface slide of head 881, or when sun gear 84 is bonded into axial restraint with the second end 51-2 of axle 51, the lower surface of sun gear 84 even can be spaced apart with the upper surface of head 881.
In the example shown in the series of figures, in head 881, groove 881a is provided with the number of number and planet wheel 86 and the jack 881b corresponding with the number of pin 89.Under the assembled state of reducing gear 80, jack 881b is positioned in axial direction align with the center hole 861 of planet wheel 86, allows pin 89 to insert in both center holes 861 of jack 881b and planet wheel 86 thus.Like this, such as, when sun gear 84 rotates, planet wheel 86 revolves round the sun around sun gear 84 while rotation, drives output shaft 88 to rotate (rotating around the spin axis consistent with the spin axis of sun gear 84) thus by pin 89.Here it should be noted that, in this application, planet wheel 86 connects also referred to as operability with this transmission joint of output shaft 88.
Under the assembled state of reducing gear 80, planet wheel 86 can be placed between the head 881 of fastening piece FP and output shaft 88 in the axial direction, and the upper surface of planet wheel 86 can with the lower surface sliding contact of fastening piece FP and the lower surface of planet wheel 86 can contact with the upper surface slide of head 881.In some instances, wear-resisting (anti-attrition) of setting example as having self-lubricating function can pad between the pair of above-mentioned sliding contact surface, and/or, above-mentioned sliding contact surface vice division chief can be made to comprise the wear-resistant material layer (such as passing through coating processes) with self-lubricating function.In some instances, additionally or alternatively, can between the pair of above-mentioned sliding contact surface charging-up lubricant oil fat etc. to guarantee smooth and easy slip.Thus, can guarantee that planet wheel 86 can realize rotating smoothly and stably and rotation while realizing axially locating.
Here, it is to be noted, also the above-mentioned same structure contributing to relative sliding can be adopted between other sliding contact surface secondary (such as, the outer surface of the inner peripheral surface of the lip part 825 of the upper surface of the bottom of sun gear 84 and the head 881 of output shaft 88 or the groove 881a at upper surface place and reducing gear housing 82 and the intermediate portion 883 of output shaft 88).
In the example shown in the series of figures, also for output shaft 88 arranges fitting 91 (being used as according to axle side limit component of the present utility model or the second axle side limit component).Fitting 91 can be provided with center hole (such as tapped hole), and fitting 91 can be threaded with the externally threaded upper curtate that is provided with of the fastening end 887 of output shaft.By adopting thread connecting mode that fitting 91 is fastened to fastening end 887, can under the prerequisite meeting fastening requirements, regulate fitting 91 relative to the location of fastening end 887 as the case may be in the axial direction.Here, it is pointed out that the above-mentioned screw thread that is fixedly not limited between fitting 91 and fastening end 887 is fixed.
In the example shown in the series of figures, reducing gear 80 is also provided with two one direction thrust bearings, such as two unilateral thrust rolling bearings---such as ball bearing (that is, upper/the first thrust-bearing 60 and under/the second thrust-bearing 62).As described in Figure 2 B, under the assembled state of reducing gear 80, the seat ring 601 of up-thrust bearing 60 abuts with the upper surface of the lip part 825 of reducing gear housing 82, and the blowout patche 605 relative with seat ring 601 abuts with the lower surface (portion 882 of topping bar) of the head 881 of output shaft 88 via ball-retainer assembly 603.In addition, as described in Figure 2 B, under the assembled state of reducing gear 80, the seat ring 621 of lower thrust-bearing 62 abuts with the lower surface of the lip part 825 of reducing gear housing 82, and the blowout patche 625 relative with seat ring 621 abuts with the upper surface of the fitting 91 of the fastening end 887 screwed to output shaft 88 via ball-retainer assembly 623.By suitably regulating the tightness of fastening piece FP and fitting 91 (such as screwing degree), can guarantee that up-thrust bearing 60 and lower thrust-bearing 62 abut with the suitable of lip part 825 of reducing gear housing 82, and other each (axis) contact surface pair (upper surface of such as planet wheel 86 and lower surface of fastening piece FP, the blowout patche 605 of up-thrust bearing 60 and the lower surface of the head 881 of output shaft 88, and the blowout patche 625 of lower thrust-bearing 62 and the upper surface of fitting 91) between the suitable suitable axial limiting abutting the output shaft 88 such as realized reducing gear 80.
In the example shown in the series of figures, consider and rotate integratedly with output shaft 88 at the operation period fitting 91 of electric expansion valve 1 and be comparatively easy to get loose, two fastening screw trip bolts (such as tapping screw) 93 can also be set.Fastening screw trip bolt 93 is fastened to the radial fastener hole (such as tapped hole) that is formed in fitting 91 and can be fastened to the fastening end 887 of output shaft 88 further by self tapping.Thus, fitting 91 can be made stably to be positioned at appropriate position relative to output shaft 88 (fastening end 887), to guarantee that fitting 91 can not come off in the length of life of electric expansion valve and guarantee the suitable abutting in reducing gear 80 between each axial Contact Pair.Here, it is pointed out that fastening screw trip bolt 93 can omit, and the number of fastening screw trip bolt 93 is not limited to two.
(outside thread) tail end/lower end 887a of the fastening end 887 of output shaft 88 can be threadedly engaged with upper curtate (internal thread part) 55-1 of anti-rotational latch 55, thus force anti-rotational latch 55 together with needle 14 to carry out axial motion by the rotation of output shaft 88 at output shaft 88 axial restraint under the fixing state of anti-rotational latch 55 circumference, realizing the opening of electric expansion valve 1, close and the adjustment of valve opening.
Here it is to be noted, in the utility model first mode of execution, form the axial limiting mechanism LM according to the output shaft 88 for reducing gear 80 of the present utility model by the lip part 825 of reducing gear housing 82, the portion of topping bar 882 (lower surface of head 881) of output shaft 88, the fitting 91 being arranged at output shaft 88, up-thrust bearing 60 and/or lower thrust-bearing 62.Top bar portion 882 is suitable for cooperatively interacting with lip part 825 and lip part 825 and fitting 91 are suitable for cooperatively interacting the axial limiting of the output shaft 88 realized reducing gear 80.Here it should be noted that, in present specification, word " (between limit component) cooperation " is intended to not only to contain the direct cooperation between the counterpart that cooperatively interacts without any intermediary component, but also contains the indirect cooperation between the counterpart that cooperatively interacts with intermediary's component.
The simple operating process described according to the electric expansion valve 1 of the utility model first mode of execution below.
When needing to open or close electric expansion valve 1 or need the valve opening regulating electric expansion valve 1, applying specific electric current to motor 40, the rotor 42 of motor 40 is rotated along specific direction (forward or backwards) together with axle 51.Along with the rotation of axle 51, the sun gear 84 of the reducing gear 80 such as engaged by key Placement with the second end 51-2 of axle 51 is also rotated along equidirectional, and the planet wheel 86 engaged with sun gear 84 also revolves round the sun along equidirectional around sun gear 84.The revolution of planet wheel 86 causes the output shaft 88 connected with planet wheel 86 via pin 89 also to rotate along equidirectional.The rotation of output shaft 88 forces the anti-rotational latch 55 be threadedly engaged with output shaft 88 to carry out axial translational movement, this so that drive needle 14 to carry out axial translational movement, realize opening or closing and the adjustment of valve opening of electric expansion valve 1 thus.
According to the utility model first mode of execution, at least following beneficial effect can be provided.
Due to adopt in the output terminal of reducing gear so-called can not manual teardown formula (axis) location/limit structure, especially adopting (axis) location/limit structure of form integratedly, there is large axial float thus cannot guarantee the situation of the accurate valve switch of electric expansion valve in the associated components (output shaft and the anti-rotational latch engaged of reducing gear) can eliminated when axial clearance is large, electric expansion valve operates in actuator.And, the large thrust load (stretch and/or compression) that reducing gear bears when operating such as all or part ofly via thrust-bearing can be offloaded on lip part and to be passed on housing further, thus avoids the gear pair in reducing gear (sun gear and planet wheel, planet wheel and interior teeth portion) directly bear large thrust load and cause gear pair to be easy to damage.
On the other hand, owing to have employed reducing gear (especially planetary gear reducing mechanism), make electric expansion valve can be adapted to large cooling capacity systems well and without the need to adopting output torque very large thus cost is very high and the motor that size (especially the size of stator) is very too fat to move.In addition, when using planetary gear reducing mechanism, shared space (especially radial space) is less and be easy to construct compact electronic expansion valve, and the reduction speed ratio (velocity ratio) that can obtain when same volume/size is also larger.
Referring to Fig. 4 A, Fig. 4 B and Fig. 4 C, reducing gear 80A according to the electric expansion valve of the utility model second mode of execution (Fig. 4 A, Fig. 4 B and Fig. 4 C are the exploded perspective view of a part for the reducing gear of the electric expansion valve illustrated according to the utility model second mode of execution, exploded perspective longitudinal section and assembled state longitudinal section respectively) is described.
In order to for simplicity, the main difference part of the second mode of execution and the first mode of execution will only be described below.
In the example shown in the series of figures, the reducing gear housing 82A of reducing gear 80A can comprise from top to bottom: engagement portion 821; Interior teeth portion 823; Lip part 825 (being used as according to case side limit component of the present utility model or the first case side limit component); Lower engagement portion (additional engagement portion) 826A (being such as screw threads for fastening portion); And auxiliary section 827.In addition, the output shaft 88A (can be considered as being equivalent to the planet carrier in typical planetary gear reducing mechanism) of reducing gear 80A can comprise from top to bottom: head 881; Upper intermediate portion 883A; Lower intermediate portion 885A; And fastening end/terminal part 887 (upper intermediate portion 883A forms intermediate portion together with lower intermediate portion 885A).The portion of topping bar 882 can be formed with between head 881 and upper intermediate portion 883A, stepped part (i.e. intermediate step portion) 886A (being used as according to axle side limit component of the present utility model or the first axle side limit component) can be formed between upper intermediate portion 883A and lower intermediate portion 885A, and stepped down part 884 can be formed with between lower intermediate portion 885A and fastening end 887.
In the example shown in the series of figures, reducing gear 80A is provided with a doubledirection thrust bearing (such as bidirectional propulsion rolling bearing---such as ball bearing) 64A.In addition, also for output shaft 88 arranges anchor log 95A (being used as according to axle side limit component of the present utility model or the second axle side limit component), anchor log 95A can be fixed to the fastening end 887 of output shaft 88A with thread connecting mode or other appropriate ways.In addition, reducing gear 80A is also provided with bounding means 97A (being used as according to case side limit component of the present utility model or the second case side limit component), and bounding means 97A can be fixed to the lower engagement portion 826A of reducing gear housing 82A with thread connecting mode or other appropriate ways.In some instances, similar with the fitting 91 in the first mode of execution, the fastening screw trip bolt (such as tapping screw) for anchor log 95A being fastened to further after being adjusted to suitable axial position at anchor log 95A fastening end 887 can be set.
As as described in Fig. 4 C, under the assembled state of reducing gear 80A, the blowout patche 641A of thrust-bearing 64A is output the intermediate step portion 886A of axle 88A and the anchor log 95A such as screwed to the fastening end 887 of output shaft 88A in the axial positions that the axial position of the lower intermediate portion 885A with output shaft 88A roughly aligns and is clipped in the middle, via upper ball-retainer assembly 643A relative with blowout patche 641A upper/the first seat ring 645A abuts with the lower surface of the lip part 825 of reducing gear housing 82A, and relative with blowout patche 641A via lower ball-retainer assembly 644A under/the second seat ring 646A abuts with the upper surface of bounding means 97A of the lower engagement portion 826A being fixedly connected to reducing gear housing 82A with such as thread connecting mode.By suitably regulating the tightness (such as screwing degree) of fastening piece FP, anchor log 95A and bounding means 97A, the suitable abutting between each (axis) contact surface pair can be guaranteed.
As shown in Figure 4 C, compare with bottom race 646A with top race 645A, blowout patche 641A more gives prominence to towards radially inner side, is convenient to thus be clipped in the middle with anchor log 95A by intermediate step portion 886A and is effectively formed and axially contact the output shaft 88A be beneficial to reducing gear 80A and carry out axial limiting.
Here it is to be noted, in the utility model second mode of execution, form the axial limiting mechanism LMA according to the output shaft 88A for reducing gear 80A of the present utility model by the intermediate step portion 886A of the lip part 825 of reducing gear housing 82A, output shaft 88A, the anchor log 95A being arranged at output shaft 88A, bounding means 97A and/or doubledirection thrust bearing 64A.
Identical with the operating process (substantially) of the electric expansion valve according to the utility model first mode of execution according to the operating process of the electric expansion valve of the utility model second mode of execution.And, can realize and the beneficial effect roughly the same according to the electric expansion valve of the utility model first mode of execution according to the electric expansion valve of the utility model second mode of execution.
Some modification are allowed according to the electric expansion valve of the utility model illustrative embodiments.
In illustrative embodiments mentioned above, describe and use unidirectional or bidirectional propulsion rolling bearing in axial limiting mechanism.But, can conceive, alternatively or additionally, sliding contact structure (use thrust slide bearing) can be adopted at least one in the axial contact surface pair of axial limiting mechanism.Such as, wear-resisting (anti-attrition) pad such as with self-lubricating function can be used, and/or, the wear-resistant material layer (such as passing through coating processes) that axial contact surface vice division chief can be made to comprise such as there is self-lubricating function, and/or, can between above-mentioned axial contact surface pair charging-up lubricant oil fat etc. to guarantee smooth and easy slip.Here, for the utility model second mode of execution, when exempting from thrust bearing 64A, the abutment flange portion being suitable for being plugged between the lip part 825 of bounding means 97A and reducing gear housing 82A can be formed at output shaft 88A place.Like this, the large thrust load (stretch and/or compression) that reducing gear bears when operating directly can be offloaded on lip part 825 and/or bounding means 97A and to be passed to further on housing.
In illustrative embodiments mentioned above, describe the use of epicyclic reduction mechanism (planetary gear reducing mechanism).But, the reducing gear of such as fixed shaft gear train reducing gear and so on also can be applied to according to axial limiting mechanism of the present utility model.
In illustrative embodiments mentioned above, describe and then export from output shaft (being equivalent to planet carrier) from sun gear input at planetary gear reducing mechanism medium power.But, can conceive, then export from the suitable component parts of other except planet carrier from the input of the suitable component parts of other except sun gear at planetary gear reducing mechanism medium power.
In illustrative embodiments mentioned above, the axial limiting mechanism described for the output terminal/output shaft of reducing gear can realize bidirectionally limited.But, in some application-specific situation, load from an axial side may be there is when valve operation comparatively large and need to carry out axial limiting and and situation of without the need to carry out axial limiting less from the load of another axial side.In this case, can conceive, make the axial limiting mechanism of the output terminal for reducing gear of the present utility model only have unidirectional limit function with correspondingly simplified structure, be reduced to principal and interest in assembling.
In present specification, directional terminology " on ", " top ", D score, " below ", " top " and " end " etc. use generally only should not be considered as being restrictive for the object being convenient to describe.
Although be described the utility model with reference to illustrative embodiments, but be to be understood that, the utility model is not limited in literary composition the concrete example/mode of execution described in detail and illustrate, when not departing from claims limited range, those skilled in the art can make various change to illustrative embodiments.
Claims (22)
1. a reducing gear (80,80A), comprising:
Reducing gear housing (82,82A);
Be arranged on the reducing gear train in described reducing gear housing (82,82A);
The output shaft (88,88A) be connected with described reducing gear train; And
Be arranged on the axial limiting mechanism (LM, LMA) in described reducing gear (80,80A),
It is characterized in that, described axial limiting mechanism (LM, LMA) comprise and be integrally formed in or be fixedly connected to described output shaft (88, axle side limit component (882 88A), 91, 886A, 95A) and be integrally formed in or be fixedly connected to described reducing gear housing (82, case side limit component (825 82A), 97A), described axle side limit component (882, 91, 886A, 95A) with described case side limit component (825, 97A) be suitable for cooperatively interacting to limit described output shaft (88, axial displacement 88A).
2. reducing gear according to claim 1 (80,80A), wherein, described reducing gear train is configured to planetary gear reducing mechanism.
3. reducing gear (80 according to claim 2,80A), wherein, described reducing gear housing (82,82A) teeth portion (823) in roughly tubular and in the inner circle wall place of described reducing gear housing (82,82A) is formed with as described planetary gear reducing mechanism gear ring.
4. reducing gear (80 according to claim 3,80A), wherein, described reducing gear train comprises sun gear (84) and planet wheel (86), external impetus inputs to described sun gear (84), a part for described output shaft (88,88A) is configured to planet carrier and operatively connects to export the moment of torsion increased because of deceleration with described planet wheel (86).
5. reducing gear (80 according to claim 4,80A), wherein, at described reducing gear housing (82, inner circle wall place 82A) is formed with engagement portion (821), described engagement portion (821) is suitable for tightening together with fastening piece (FP), described fastening piece (FP) is suitable for keeping described planet wheel (86) and/or described sun gear (84) together with described output shaft (88,88A).
6. reducing gear according to claim 5 (80,80A), wherein, described fastening piece (FP) is threaded connection and is fastened to described engagement portion (821) with axial adjustable way.
7. reducing gear according to any one of claim 1 to 6 (80,80A), wherein, described axial limiting mechanism (LM, LMA) also comprises thrust bearing (60,62,64A).
8. reducing gear according to claim 7 (80), wherein, described thrust bearing (60,62) for being arranged on described axle side limit component (882,91) the unilateral thrust rolling bearing (60,62) and between described case side limit component (825).
9. reducing gear according to claim 8 (80), wherein,
Described axle side limit component (882,91) comprises the first axle side limit component (882) and the second axle side limit component (91),
Described output shaft (88) comprises head (881), intermediate portion (883) and terminal part (887), the stepped part (882) as described first axle side limit component (882) is formed between described head (881) and described intermediate portion (883), the fitting (91) as described second axle side limit component (91) is fastened with at described terminal part (887) place, and
The lip part (825) be placed between described stepped part (882) and described fitting (91) as described case side limit component (825) is formed at the inner circle wall place of described reducing gear housing (82).
10. reducing gear according to claim 9 (80), wherein, described unilateral thrust rolling bearing (60,62) comprises the first unilateral thrust rolling bearing (60) be arranged between described stepped part (882) and described lip part (825) and the second unilateral thrust rolling bearing (62) be arranged between described lip part (825) and described fitting (91).
11. reducing gears according to claim 9 (80), wherein, described fitting (91) is threaded connection and is fastened to described terminal part (887) with axial adjustable way.
12. reducing gears according to claim 11 (80), also comprise the fastening screw trip bolt (93) for described fitting (91) being fastened to further described terminal part (887).
13. reducing gears according to claim 7 (80A), wherein, described thrust bearing (64A) is bidirectional propulsion rolling bearing (64A).
14. reducing gears according to claim 13 (80A), wherein,
Described axle side limit component (886A, 95A) comprise the first axle side limit component (886A) and the second axle side limit component (95A), and described case side limit component (825,97A) comprise the first case side limit component (825) and the second case side limit component (97A)
Described output shaft (88A) comprises head (881), intermediate portion (883A, 885A) with terminal part (887), at described intermediate portion (883A, 885A) place is formed with the stepped part (886A) as described first axle side limit component (886A), the anchor log (95A) as described second axle side limit component (95A) is fastened with at described terminal part (887) place, and
Be formed with the lip part (825) as described first case side limit component (825) at the inner circle wall place of described reducing gear housing (82A), and be fastened with the bounding means (97A) as described second case side limit component (97A) at the inner circle wall place of described reducing gear housing (82A).
15. reducing gears according to claim 14 (80A), wherein, described bidirectional propulsion rolling bearing (64A) is arranged between described lip part (825) and described bounding means (97A), and the middle blowout patche (641A) that is positioned at of described bidirectional propulsion rolling bearing (64A) is compared more outstanding towards radially inner side with first seat ring (645A) being positioned at two ends of described bidirectional propulsion rolling bearing (64A) with the second seat ring (646A), described blowout patche (641A) is made to be suitable for being clipped in the middle by described stepped part (886A) and described anchor log (95A).
16. reducing gears (80 according to claim 14,80A), wherein, described anchor log (95A) is threaded connection and is fastened to described terminal part (887) with axial adjustable way, and/or described bounding means (97A) is threaded connection the inner circle wall being fastened to described reducing gear housing (82A) with axial adjustable way.
17. reducing gears according to any one of claim 1 to 6 (80,80A), wherein, described axial limiting mechanism (LM, LMA) also comprises thrust slide bearing.
18. reducing gears according to claim 17 (80,80A), wherein, described axle side limit component (882,91,886A, 95A) with described case side limit component (825,97A) in the following way in one or more modes realize being slidably matched:
A) between described axle side limit component (882,91,886A, 95A) Yu described case side limit component (825,97A), the wear-resistant pad with self-lubricating function is provided with,
The surface of at least one b) in described axle side limit component (882,91,886A, 95A) and described case side limit component (825,97A) is coated with the wear-resistant material layer with self-lubricating function, and
C) charging-up lubricant oil fat between described axle side limit component (882,91,886A, 95A) Yu described case side limit component (825,97A).
19. 1 kinds of electric expansion valves (1), comprising:
Frame set (CA);
Valve assembly (10), described valve assembly (10) comprises movable valve member (14) and for regulating the flow of the fluid flowing through described electric expansion valve (1);
Actuator (50), described actuator (50) carries out axial motion for driving described movable valve member (14); And
Driving mechanism (40), described driving mechanism (40) for providing power to described actuator (50),
It is characterized in that, described actuator (50) comprises the reducing gear (80 according to any one of claim 1 to 18,80A), described actuator (50) is via described reducing gear (80, output shaft (88,88A) 80A) drives described movable valve member (14) to carry out axial motion.
20. electric expansion valves according to claim 19 (1), wherein, described reducing gear housing (82,82A) forms the integral part of described frame set (CA).
21. electric expansion valves according to claim 19 (1), also comprise the sleeve (44) of the part forming described frame set (CA), wherein, described reducing gear housing (82,82A) be contained in together with the rotor (42) of described driving mechanism (40) in described sleeve (44), and described reducing gear housing (82,82A) is fixedly connected to described sleeve (44).
22. electric expansion valves according to claim 19 (1), wherein, the outside of described reducing gear housing (82,82A) is exposed to external environment condition and is connected with the counterpart member in other component of a part for the described frame set of formation (CA).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520012787.3U CN204533762U (en) | 2015-01-08 | 2015-01-08 | Speed reducing mechanism and electronic expansion valve comprising same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520012787.3U CN204533762U (en) | 2015-01-08 | 2015-01-08 | Speed reducing mechanism and electronic expansion valve comprising same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204533762U true CN204533762U (en) | 2015-08-05 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520012787.3U Withdrawn - After Issue CN204533762U (en) | 2015-01-08 | 2015-01-08 | Speed reducing mechanism and electronic expansion valve comprising same |
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| Country | Link |
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| CN (1) | CN204533762U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105822822A (en) * | 2015-01-08 | 2016-08-03 | 艾默生环境优化技术(苏州)有限公司 | Speed reducing mechanism and electronic expansion valve comprising same |
| WO2019105454A1 (en) * | 2017-12-01 | 2019-06-06 | 浙江三花智能控制股份有限公司 | Electronic expansion valve and cooling system having same |
| EP3719365A4 (en) * | 2017-12-01 | 2021-08-18 | Zhejiang Sanhua Intelligent Controls Co., Ltd. | Electronic expansion valve and cooling system having same |
| JP7034527B1 (en) * | 2020-07-10 | 2022-03-14 | 株式会社不二工機 | Solenoid valve |
-
2015
- 2015-01-08 CN CN201520012787.3U patent/CN204533762U/en not_active Withdrawn - After Issue
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105822822A (en) * | 2015-01-08 | 2016-08-03 | 艾默生环境优化技术(苏州)有限公司 | Speed reducing mechanism and electronic expansion valve comprising same |
| CN105822822B (en) * | 2015-01-08 | 2019-08-06 | 艾默生环境优化技术(苏州)有限公司 | Speed reducing mechanism and electronic expansion valve comprising same |
| WO2019105454A1 (en) * | 2017-12-01 | 2019-06-06 | 浙江三花智能控制股份有限公司 | Electronic expansion valve and cooling system having same |
| EP3719365A4 (en) * | 2017-12-01 | 2021-08-18 | Zhejiang Sanhua Intelligent Controls Co., Ltd. | Electronic expansion valve and cooling system having same |
| US11168804B2 (en) | 2017-12-01 | 2021-11-09 | Zhejiang Sanhua Intelligent Controls Co., Ltd. | Electronic expansion valve and cooling system having same |
| JP7034527B1 (en) * | 2020-07-10 | 2022-03-14 | 株式会社不二工機 | Solenoid valve |
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