CN201327255Y - Electric expansion valve and refrigeration circulation system - Google Patents
Electric expansion valve and refrigeration circulation system Download PDFInfo
- Publication number
- CN201327255Y CN201327255Y CNU2008201343511U CN200820134351U CN201327255Y CN 201327255 Y CN201327255 Y CN 201327255Y CN U2008201343511 U CNU2008201343511 U CN U2008201343511U CN 200820134351 U CN200820134351 U CN 200820134351U CN 201327255 Y CN201327255 Y CN 201327255Y
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- spool
- refrigerant
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- armature spindle
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- 238000005057 refrigeration Methods 0.000 title abstract description 4
- 239000003507 refrigerant Substances 0.000 claims description 106
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical group O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 12
- 238000006073 displacement reaction Methods 0.000 claims description 7
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 6
- 239000001569 carbon dioxide Substances 0.000 claims description 6
- 230000015572 biosynthetic process Effects 0.000 claims description 3
- 230000033001 locomotion Effects 0.000 claims description 2
- 238000000926 separation method Methods 0.000 claims description 2
- 239000002826 coolant Substances 0.000 abstract description 9
- 210000000038 chest Anatomy 0.000 description 11
- 230000000694 effects Effects 0.000 description 10
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- JEIPFZHSYJVQDO-UHFFFAOYSA-N ferric oxide Chemical compound O=[Fe]O[Fe]=O JEIPFZHSYJVQDO-UHFFFAOYSA-N 0.000 description 6
- 238000012856 packing Methods 0.000 description 6
- 238000001816 cooling Methods 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000001174 ascending effect Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 230000005405 multipole Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000001007 puffing effect Effects 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000010257 thawing Methods 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Electrically Driven Valve-Operating Means (AREA)
Abstract
The utility model relates to a topic of providing an electric expansion valve and a refrigeration circulation system, wherein, the flow-rate of a cooling medium can be normally controlled both at a positive flow direction and a reverse flow direction of the electric expansion valve in the heat-pump-type refrigeration circulation system. A valve core is kept and slides freely in a cylinder of a supporting component; a jogged hole is utilized to be connected with a rotor shaft of a step motor and the valve core; a projection part of the rotor shaft is opposite to the bottom of the jogged hole; the upper head face of a flange part is opposite to the lower head face of a gasket; a gap is formed between the jogged hole and the rotor shaft; the valve core can shift relatively at an axle direction relative to the rotor shaft; when in the positive flow direction that the cooling medium sequentially flows through a first cooling medium tube, a valve chamber and a second cooling medium, the pressure of the cooling medium leads the gasket to be buckled with the flange part, thereby leading the valve core and the rotor shaft to be driven integrally; and when in the reverse flow direction, the pressure of the cooling medium leads the bottom to be buckled with the projection part, so as to lead the valve core and the rotor shaft to be driven integrally.
Description
Technical field
The utility model relates to the electric expansion valve that sets as expansion valve and has used the refrigerating circulation system of this electric expansion valve between the outdoor heat exchanger of thermal pump type refrigerating circulation system and indoor heat exchanger.
Background technology
All the time, in thermal pump type refrigerating circulation system, between outdoor heat exchanger and indoor heat exchanger, be provided with expansion valve, when refrigeration mode, make from guiding indoor heat exchanger after the refrigerant expansion of outdoor heat exchanger with expansion valve; When being in the heating pattern, make from guide chamber external heat exchanger after the refrigerant expansion of indoor heat exchanger with expansion valve.As this expansion valve, in order to tackle normal operation, defrosting running, dehumidifying running etc., the various schemes that propose to have the amount of restriction (cold medium flux) of control refrigerant are (with reference to patent documentation 1: TOHKEMY 2003-148643 communique, patent documentation 2: TOHKEMY 2003-329157 communique).
Should existing expansion valve, spool is set in valve chamber and has fixed the valve support of this spool, this valve bracket clamp is fixed on the end of armature spindle of stepper motor, and with another refrigerant pipe position adjacent of valve chamber on the valve base part relative with spool is set.And, by the rotary rotor axle spool is moved relative to valve base part at axis direction (above-below direction), and quantitatively increase and decrease the switching and the effective vent area of the valve port of this valve base part, thereby controlling the flow of refrigerant.In addition, be provided with compression helical spring, obtain the cushioning effect of spool when falling to being positioned at valve base part by this compression helical spring with the relative rotor axial valve base part one side reinforcing of spool with vavle shelf.
In above-mentioned existing expansion valve, use compression helical spring owing between armature spindle and spool, possess buffering, thereby there are the following problems.Though do not have problems from valve chamber flows out (just flowing to) between valve port and spool occasion at refrigerant, but under the situation of flow (reverse direction flow) that flow into valve chamber as refrigerant from the refrigerant pipe (pipe joint) of valve base part one side from the gap of valve port and spool, surpass the occasion of the active force of compression helical spring at the pressure of this refrigerant, spool moves and produces the unstable phenomenon (swing) of spool from valve port.Thus, there is the situation that to carry out normal flow-control because of changes in flow rate.Especially, in the refrigerating circulation system of the super-pressure refrigerant that uses carbon dioxide as refrigerant, become problem.
The utility model content
So no matter problem of the present utility model provides is the electric expansion valve and the refrigerating circulation system that just flow to or all can normally carry out in reverse direction flow flow-control at refrigerant.
The electric expansion valve of scheme one possesses: valve chest, this valve chest form valve chamber and connect the first refrigerant pipe and the second refrigerant pipe that is communicated with this valve chamber; Valve seat, this valve seat have the valve port that is provided between above-mentioned valve chamber and the above-mentioned second refrigerant pipe; Spool, thus this spool is disposed in the above-mentioned valve chamber and above-mentioned relatively valve port carries out the aperture variation that contact separation makes this valve port; And driving mechanism, thereby this driving mechanism moves this rotor axial and then this spool of motorized motions by rotating the armature spindle that links with above-mentioned spool at the direction of principal axis of above-mentioned valve port, for the refrigerant of the above-mentioned first refrigerant pipe is that the refrigerant of high pressure and the above-mentioned second refrigerant pipe is that the first-class of refrigerant of low pressure is that the refrigerant of high pressure and the above-mentioned first refrigerant pipe is second each flow direction that flows to of the refrigerant of low pressure to the refrigerant with the above-mentioned second refrigerant pipe, control the flow of this refrigerant by the aperture of above-mentioned valve port, it is characterized in that, above-mentioned spool is supported slidably freely on the direction of principal axis of above-mentioned valve port by the support component that is fixed on the above-mentioned valve chest, and in the mode of the above-mentioned relatively armature spindle of this spool displacement relatively on above-mentioned direction of principal axis this spool and this armature spindle are linked, the linking portion of this spool and this armature spindle has: in the first fastening portion of this spool of position fastening of the most close valve port one side of relative this armature spindle of this spool; And this spool relatively this armature spindle away from the second fastening portion of this spool of position fastening of valve port, above-mentioned first-class to the time, by by the differential pressure of the above-mentioned valve chamber and the refrigerant of the above-mentioned second refrigerant pipe with above-mentioned spool with the above-mentioned first fastening portion relative above-mentioned armature spindle holding position, thereby this armature spindle and this spool are moved integratedly, control this first-class to flow, when above-mentioned second flows to, by by the differential pressure of the refrigerant of above-mentioned second refrigerant pipe and above-mentioned valve chamber with above-mentioned spool with the above-mentioned second fastening portion relative above-mentioned armature spindle holding position, thereby this armature spindle and this spool are moved integratedly, control this second flow that flows to.
The electric expansion valve of scheme two, on the basis of the electric expansion valve of scheme one, it is characterized in that, the set positions of the mobile terminal of the above-mentioned valve seat direction of above-mentioned armature spindle becomes the position of following mobile terminal: promptly, above-mentioned first-class to the time, this spool is with the above-mentioned first fastening portion holding position under above-mentioned spool and the non-contacting state of above-mentioned valve seat, and when above-mentioned second flowed to, this spool was with the above-mentioned second fastening portion holding position.
The electric expansion valve of scheme three, on the basis of the electric expansion valve of scheme one, it is characterized in that, the set positions of the mobile terminal of the above-mentioned valve seat direction of above-mentioned armature spindle becomes the position of following mobile terminal: promptly, above-mentioned first-class to the time, fall to being positioned under the state of above-mentioned valve seat this spool at above-mentioned spool not by above-mentioned first fastening portion and the fastening of the above-mentioned second fastening portion, and when above-mentioned second flowed to, this spool was with the above-mentioned second fastening portion holding position.
The refrigerating circulation system of scheme four is characterized in that, the electric expansion valve described in the plan of establishment one, two or three in the runner of the refrigerant between indoor heat exchanger and outdoor heat exchanger.
The refrigerating circulation system of the 5th scheme on the basis of the refrigerating circulation system of scheme four, is characterized in that above-mentioned refrigerant is a carbon dioxide.
Effect of the present utility model is as follows:
Electric expansion valve according to scheme one, since no matter be just flowing to or reverse direction flow by the differential pressure difference of refrigerant with the relative armature spindle of spool holding position, armature spindle and spool are moved with becoming one, the flow of control refrigerant, therefore can not produce the unstable phenomenon (swing) of the spool that the differential pressure because of refrigerant causes, can normally control flow.
According to the electric expansion valve of scheme two, not only has the effect of scheme one, also just flowing to and control that the both sides of reverse direction flow all can make refrigerant less flow to refrigerant.
According to the electric expansion valve of scheme three, not only has the effect of scheme one, the control that refrigerant is less flowed.
According to the refrigerating circulation system of scheme four, with first scheme in the same manner, just flowing to and control that the both sides of reverse direction flow all can make refrigerant less flow for refrigerant.
According to the refrigerating circulation system of scheme five, utilize super-pressure carbon dioxide refrigerant relatively armature spindle spool carried out the position reliably keep, can further normally control flow.
Description of drawings
Fig. 1 (A), Fig. 1 (B) are respectively the longitudinal sectional view and the partial enlarged drawing of the electric expansion valve of the utility model embodiment.
Fig. 2 is the figure of the thermal pump type refrigerating circulation system of expression the utility model embodiment.
Fig. 3 (A), Fig. 3 (B) are the figure that the armature spindle of first embodiment that expression relates to the control action of the electric expansion valve that has used the utility model embodiment is positioned at the state of lowest positions.
Fig. 4 (A), Fig. 4 (B) are the figure of the state after the armature spindle of expression first embodiment and second embodiment rises from lowest positions.
Fig. 5 is the figure of the relation of the expression umber of pulse of first embodiment and flow, among the figure, X: spool that is just flowing to and the contact position of valve seat (imaginary positions), Y: the spool of reverse direction flow and the contact position of valve seat (imaginary positions), Z: the origin position of the direction of rotation of rotor (0 pulse: lowest positions).
Fig. 6 (A), Fig. 6 (B) are the figure that the armature spindle of second embodiment that expression relates to the control action of the electric expansion valve that has used the utility model embodiment is positioned at the state of lowest positions.
Fig. 7 is the figure of the relation of the expression umber of pulse of second embodiment and flow, among the figure, X: spool that is just flowing to and the contact position of valve seat (imaginary positions), Y: the spool of reverse direction flow and the contact position of valve seat, Z: the origin position of the direction of rotation of rotor (0 pulse: lowest positions).
Among the figure:
The 1-valve chest, 1A-valve chamber, the 11-first refrigerant pipe, the 12-second refrigerant pipe, the 2-valve seat, 21-valve port, 3-support component, 4-spool, the 42-embedded hole, 42a-bottom (the second fastening portion), 43-packing ring, 43a-lower surface (the first fastening portion), the 5-stepper motor, 51-armature spindle, 51a-flange part, 51b-protuberance (the second fastening portion), 51c-upper surface (the first fastening portion), 10-electric expansion valve, 20-outdoor heat exchanger, the 30-indoor heat exchanger, 40-flow channel switching valve, 50-compressor.
The specific embodiment
Below, with reference to the embodiment of description of drawings electric expansion valve of the present utility model and refrigerating circulation system.Fig. 1 (A), Fig. 1 (B) are respectively the longitudinal sectional view (Fig. 1 (A)) and the partial enlarged drawings (Fig. 1 (B)) of the electric expansion valve of embodiment, and Fig. 2 is the figure that the thermal pump type refrigerating circulation system of this expansion valve 10 has been used in expression.In addition, the notion of " up and down " in the following description and accompanying drawing is corresponding up and down.
In Fig. 2, symbol 10 is electric expansion valves of embodiment of the present utility model, the 20th, carry the outdoor heat exchanger on outdoor unit, and the 30th, carry the indoor heat exchanger on indoor unit, the 40th, the flow channel switching valve of formation cross valve, the 50th, compressor.Electric expansion valve 10, outdoor heat exchanger 20, indoor heat exchanger 30, flow channel switching valve 40 and compressor 50 connect as shown by conduit separately like that, constitute the refrigerating circulation system of heat-pump-type.In addition, accumulator, pressure sensor, temperature sensor etc. omit diagram.
Runner when runner the when runner of refrigerating circulation system is cooling operation by flow channel switching valve 40 bi-directional conversion and heating running.When cooling operation, as using in the drawings shown in the solid arrow, flow into outdoor heat exchanger 20 with the refrigerant after compressor 50 compressions from flow channel switching valve 40, this outdoor heat exchanger 20 plays a role as condenser, the cooling medium liquid that flows out from outdoor heat exchanger 20 flows into indoor heat exchangers 30 by electric expansion valve 10, and this indoor heat exchanger 30 plays a role as evaporimeter.On the other hand, when warming oneself running, shown in dashed lines arrow in the drawings, with the refrigerant after compressor 50 compression from the sequential loop of flow channel switching valve 40 with indoor heat exchanger 30, electric expansion valve 10, outdoor heat exchanger 20, flow channel switching valve 40 and compressor 50, indoor heat exchanger 30 plays a role as condenser, and outdoor heat exchanger 20 plays a role as evaporimeter.10 pairs of electric expansion valves carry out puffing respectively from the cooling medium liquid of outdoor heat exchanger 20 inflows or the cooling medium liquid that flows into from indoor heat exchanger 30 when heating is turned round when cooling operation, control the flow of this refrigerant again.In addition, the refrigerant as the refrigerating circulation system of present embodiment uses the super-pressure carbon dioxide.
Below, the electric expansion valve 10 of embodiment is described based on Fig. 1 (A), Fig. 1 (B).Electric expansion valve 10 has the valve chest 1 of drum.Valve chest 1 has the 1a of draw portion that the one side end is dwindled caliber and form, and the valve seat 2 with the conglobate valve port 21 of opening is installed in the 1a of this draw portion.In addition, the peristome in the side opposite with the 1a of draw portion of valve chest 1 is equipped with support component 3.Thus, valve casing 1 side formation within it valve chamber 1A.At the first refrigerant pipe 11 that the one-sided connection of the periphery of valve chest 1 is communicated with outdoor heat exchanger 20, this first refrigerant pipe 11 is connected with valve chamber 1A.In addition, at the second refrigerant pipe 12 of the 1a of draw portion connection with indoor heat exchanger 30, this second refrigerant pipe 12 is connected with valve chamber 1A by the valve port 21 of valve seat 2.In addition, this first refrigerant pipe 11, the second refrigerant pipe 12, support component 3 meet (La by wax and pay け) etc. be fixed on the valve chest 1.
Spool 4 has the pin portion 41 of cone shape in the bottom of valve seat 2 sides, and has the embedded hole 42 that makes cylindrical hole in the end with these pin portion 41 opposite sides.And spool 4 cooperates with the armature spindle 51 of following stepper motor 5 in embedded hole 42.And spool 4 is moved in valve chamber 1A by armature spindle 51, thereby by making pin portion 41 insert or leave valve port 21 aperture of valve port 21 is changed.Thus, control flow to from the first refrigerant pipe 11 the second refrigerant pipe 12 refrigerant flow or flow to the flow of the refrigerant of the first refrigerant pipe 11 from the second refrigerant pipe 12.
Be formed with flange part 51a in the bottom of armature spindle 51, the part of this flange part 51a is inserted and is entrenched in the embedded hole 42.In addition, the open side at embedded hole 42 is equipped with packing ring 43.Have again, be formed with the protuberance 51b also more outstanding a little in the lower end of armature spindle 51 than flange part 51a.This protuberance 51b is relative with the bottom 42a of embedded hole 42.In addition, the upper surface 51c of flange part 51a is relative with the lower surface 43a of packing ring 43.
And, between embedded hole 42 and armature spindle 51, be formed with certain clearance C.Thus, spool 4 armature spindle 51 displacement relatively on axle L direction relatively.Promptly, when spool 4 relative armature spindles 51 are displaced to bottom, the lower surface 43a butt of the upper surface 51c of flange part 51a and packing ring 43, the displacement of relative armature spindle 51 downward directions of spool 4 is by fastening.In addition, when spool 4 relative armature spindles 51 are indexed to topmost, protuberance 51b and bottom 42a butt, the relative armature spindle 51 of spool 4 upward to displacement by fastening.In addition, always keep with pressing by the balancing orifice 3a that is formed on the support component 3 in the embedded hole 42 with valve chamber 1A.
Like this, with spool 4 relatively the mode spool 4 of armature spindle 51 displacement relatively on axle L direction be attached at armature spindle 51.The upper surface 51c of flange part 51a and the lower surface 43a of packing ring 43 become in " the first fastening portion " of spool 4 with respect to position (bottom) the fastening spool 4 of armature spindle 51 the most close valve port 21 1 sides.In addition, the bottom 42a of the protuberance 51b of armature spindle 51 and embedded hole 42 becomes at spool 4 relative armature spindles 51 away from " the second fastening portion " of position (topmost) the fastening spool 4 of valve port 21.
Be formed with external thread part 511 on armature spindle 51, this external thread part 511 combines with internal thread part 32a screw thread on being formed at support component 3.Thus, armature spindle 51 is mobile on axle L line direction with rotation.
The shell 52 that is fixed with airtightly as the stepper motor 5 of drive division is waited in upper end at valve chest 1 by welding.In shell 52, rotatably be provided with peripheral part the magnet rotor 53 after multipole magnetized, on this magnet rotor 53, install and fix armature spindle 51.In addition, in this shell 52, be provided with the guide 52a cylindraceous that hangs down from its top, in this guide 52a, be equipped with parts of bearings 54 cylindraceous.And the upper end of armature spindle 51 rotatably is entrenched on the parts of bearings 54.
In addition, be equipped with stator coil 55, thereby make magnet rotor 53 rotations by stator coil 55 being given pulse signal according to this umber of pulse as the stepper motor 5 of drive division in the periphery of shell 52.And the armature spindle 51 that forms one with magnet rotor 53 rotates because of the rotation of this magnet rotor 53, and moves by the axle L direction of following this rotor rotated axle 51, and spool 4 moves on axle L direction.
Have again, in shell 52, be provided with the spirally-guided line body 56 that is installed in guide 52a periphery, the movable brake component 57 that cooperates with spirally-guided line body 56 spirals.On magnet rotor 53, form jut 53a, follow the rotation of magnet rotor 53 to play to change movable brake component 57, thereby while movable brake component 57 rotates owing to cooperate with the spiral of spirally-guided line body 56 moves up and down by jut 53a.And, the detent 56a butt of movable brake component 57 and the lower end side of spirally-guided line body 56, thus rotation brake effect can be obtained in the lowest positions of armature spindle 51.
Here, the lowest positions of armature spindle 51 is set by movable brake component 57 and detent 56a.In addition, because stepper motor 5 drives by pulse signal as mentioned above like that, so it is corresponding with the rotation amount ascending amount of armature spindle 51 to begin the umber of pulse of the pulse signal that applied when armature spindle 51 is positioned at lowest positions.And the flow of refrigerant is according to this umber of pulse correspondence.
Below, the effect of the electric expansion valve 10 of embodiment is described according to the embodiment that relates to control action.In addition, refrigerant flowed into and just be decided to be from the direction that the second refrigerant pipe 12 flows out from the first refrigerant pipe 11 flow to, refrigerant is flowed into and the direction that flows out from the first refrigerant pipe 11 is decided to be reverse direction flow from the second refrigerant pipe 12.
Fig. 3 (A)～Fig. 5 is the figure of first embodiment that expression relates to the control action of the electric expansion valve 10 that has used embodiment, Fig. 3 (A), Fig. 3 (B) are the figure that expression armature spindle 51 is positioned at the lowest positions state, Fig. 4 (A), Fig. 4 (B) are the figure of the state after expression armature spindle 51 rises from lowest positions, and Fig. 5 is the figure of indicating impulse number and discharge relation.Fig. 3 (A) and Fig. 4 (A) expression just flow to, Fig. 3 (B) and Fig. 4 (B) expression reverse direction flow.This first embodiment is at armature spindle 51 under the state of lowest positions, is just flowing to and arbitrary occasion of reverse direction flow, and spool 4 all is in the state of having opened valve port 21.In addition, in Fig. 5, X point, the Y point of the contact position of expression spool 4 and valve seat 2 are imaginary points.
Promptly, in arbitrary occasion of Fig. 3 (A) and Fig. 3 (B), armature spindle 51 all is in identical lowest positions.In the occasion of Fig. 3 (A), the pressure (pressure of valve chamber 1A) of the refrigerant that flows into from the first refrigerant pipe 11 becomes than the pressure height of the refrigerant that flows out from the second refrigerant pipe 12, by the differential pressure of this pressure to the power f of spool 4 effects to valve port 21 sides.Thus, spool 4 by fastening, and forms very little clearance D by the relative armature spindle of the first fastening portion (the upper surface 51c of flange part 51a and the lower surface 43a of packing ring 43) 51 between spool 4 and valve port 21.
In the occasion of Fig. 3 (B), the pressure of the refrigerant that flows into from the second refrigerant pipe 12 becomes than pressure (pressure of the valve chamber 1A) height of the refrigerant that flows out from the first refrigerant pipe 11, the differential pressure by this pressure to spool 4 effects to the power-f of valve port 21 opposite sides.Thus, spool 4 by fastening, and forms the big gap B of ratio gap D by the relative armature spindle of the second fastening portion (the protuberance 51b of armature spindle 51 and the bottom 42a of embedded hole 42) 51 between spool 4 and valve port 21.In addition, between clearance C, D, B, set up the relation of C=B-D.
If armature spindle 51 is risen from the state of Fig. 3 (A), Fig. 3 (B), then be in the state of Fig. 4 (A), Fig. 4 (B), in the arbitrary occasion that just flows to (Fig. 4 (A)) and reverse direction flow (Fig. 4 (B)), to spool 4 active force f and power-f, spool 4 rises integratedly with armature spindle 51 by the differential pressure of above-mentioned identical refrigerant.And, between spool 4 and valve port 21, when just flowing to, produce gap E, when reverse direction flow, produce gap F.In this case, between gap E, F, set up the relation of C=F-E.
Fig. 6 (A), Fig. 6 (B) and Fig. 7 are the figure of second embodiment that expression relates to the control action of the electric expansion valve 10 that has used embodiment, Fig. 6 (A), Fig. 6 (B) are the figure that expression armature spindle 51 is positioned at the state of lowest positions, and Fig. 7 is the figure of indicating impulse number and discharge relation.In addition, with first embodiment in the same manner, Fig. 6 (A) expression just flows to, Fig. 6 (B) represents reverse direction flow.This second embodiment is at armature spindle 51 under the state of lowest positions, and when just flowing to, valve port 21 is in the state of contract fully by spool 4; When reverse direction flow, valve port 21 is in the state of opening by spool 4.In addition, in Fig. 7, the X point of the contact position of expression spool 4 and valve seat 2 is imaginary points.
In the occasion of this second embodiment, also the differential pressure because of refrigerant is just flowing to (Fig. 6 (A)) to the power f of spool 4 effects to valve port 21 sides, and at lowest positions spool 4 and valve seat 2 butts, thereby make valve port 21 be in the state of contract fully.In addition, reverse direction flow (Fig. 6 (B)) to spool 4 effect to the power-f of valve port 21 opposite sides, spool 4 by the relative armature spindle of the second fastening portion 51 by fastening.And, between spool 4 and valve port 21, form gap B.In addition, between the gap A of the first fastening portion of Fig. 6 (A) and clearance C, B, set up the relation of C=A+B.In addition, if armature spindle 51 is risen from the state of Fig. 6 (A), Fig. 6 (B), then be in the state of Fig. 4 (A), Fig. 4 (B) in the same manner with first embodiment, and in this occasion, also because of above-mentioned identical differential pressure to spool 4 active force f and power-f, spool 4 rises integratedly with armature spindle 51.
Occasion at this second embodiment, when just flowing to and when closing the driving of valve direction, the umber of pulse of stepper motor 5 be 0 pulse (state of Fig. 6 (A)) before, spool 4 falls to being positioned on the valve seat 2, and at this moment at the gapped B+A=C of the second fastening portion (between the protuberance 51b of armature spindle 51 and the bottom 42a of embedded hole 42), even if armature spindle 51 is still descended, the gap of this second fastening portion also is maintained to minimal B, therefore, the pin portion 41 of spool 4 can not be trapped in the valve port 21.
Like this, when just flowing to, because of the differential pressure of the refrigerant of the valve chamber 1A and the second refrigerant pipe 12, spool 4 usefulness, the first fastening portion relative armature spindle 51 holding positions, and armature spindle 51 and spool 4 move integratedly, thus the flow of control refrigerant.Similarly, when reverse direction flow, because of the differential pressure of the refrigerant of the second refrigerant pipe 12 and valve chamber 1A, the spool 4 usefulness second fastening portion is with respect to armature spindle 51 holding positions, and armature spindle 51 and spool 4 move integratedly, thus the flow of control refrigerant.
In addition, when so moving valve core 4 is controlled flows, because this spool 4 always moves integratedly with armature spindle 51, therefore, even spool 4 and armature spindle 51 displacement relatively on the axle L of valve port 21 direction, can not produce the unstable phenomenon (swing) of the spool 4 that the pressure differential because of refrigerant causes yet, can normally control flow.Especially, the occasion at the super-pressure refrigerant that uses carbon dioxide is equivalent to the bigger amount of differential pressure with the power grow of spool 4 fastenings on armature spindle 51, thereby fastening spool 4 securely can normally be controlled flow.
In first embodiment and second embodiment, difference only is the setting difference of the lowest positions of armature spindle 51.And in the electric expansion valve 10 of first embodiment, the lowest positions of armature spindle 51 is set as follows.Promptly, set the lowest positions of armature spindle 51 as follows: when just flowing to shown in Fig. 3 (A), in spool 4 and the valve seat 2 non-contacting state bottom spool 4 usefulness first fastening portion holding position, and when the reverse direction flow shown in Fig. 3 (B), the spool 4 usefulness second fastening portion holding position.Thus, for just flowing to and the both sides of reverse direction flow, all can control so that refrigerant less flows.
In addition, in the electric expansion valve 10 of second embodiment, the lowest positions of armature spindle 51 is set as follows.Promptly, set the lowest positions of armature spindle 51 as follows: when just flowing to shown in Fig. 6 (A), fall to being positioned at the state bottom spool 4 of valve seat 2 not by the first fastening portion and the fastening of second institute of fastening portion at spool 4, and when the reverse direction flow shown in Fig. 6 (B), the spool 4 usefulness second fastening portion holding position.Thus, when reverse direction flow, can control so that refrigerant less flows.
Claims (3)
1. an electric expansion valve possesses:valve chest, the first refrigerant pipe and the second refrigerant pipe that this valve chest formation valve chamber and connection are communicated with this valve chamber; Valve seat, this valve seat have the valve port that is provided between above-mentioned valve chamber and the above-mentioned second refrigerant pipe; Spool, thus this spool is disposed in the above-mentioned valve chamber and above-mentioned relatively valve port carries out the aperture variation that contact separation makes this valve port; And driving mechanism; Thereby this driving mechanism by rotate the armature spindle that links with above-mentioned spool the direction of principal axis of above-mentioned valve port move this armature spindle to so that this spool of motorized motions; For the refrigerant of above-mentioned first refrigerant pipe be the refrigerant of high pressure and above-mentioned second refrigerant pipe be low pressure refrigerant first-class to the refrigerant with above-mentioned second refrigerant pipe be the refrigerant of high pressure and above-mentioned first refrigerant pipe be low pressure refrigerant second to every flow to; Controlled the flow of this refrigerant by the aperture of above-mentioned valve port; It is characterized in that
Above-mentioned spool is supported slidably freely on the direction of principal axis of above-mentioned valve port by the support component that is fixed on the above-mentioned valve chest, and in the mode of the above-mentioned relatively armature spindle of this spool displacement relatively on above-mentioned direction of principal axis this spool and this armature spindle is linked,
The linking portion of this spool and this armature spindle has: in the first fastening portion of this spool of position fastening of the most close valve port one side of relative this armature spindle of this spool; And this spool relatively this armature spindle away from the second fastening portion of this spool of position fastening of valve port,
Above-mentioned first-class to the time, by by the differential pressure of the above-mentioned valve chamber and the refrigerant of the above-mentioned second refrigerant pipe with above-mentioned spool with the above-mentioned first fastening portion relative above-mentioned armature spindle holding position, thereby this armature spindle and this spool are moved integratedly, control this first-class to flow
When above-mentioned second flows to, by by the differential pressure of the refrigerant of above-mentioned second refrigerant pipe and above-mentioned valve chamber with above-mentioned spool with the above-mentioned second fastening portion relative above-mentioned armature spindle holding position, thereby this armature spindle and this spool are moved integratedly, control this second flow that flows to.
2. a refrigerating circulation system is characterized in that,
The described electric expansion valve of claim 1 is set in the runner of the refrigerant between indoor heat exchanger and outdoor heat exchanger.
3. refrigerating circulation system according to claim 2 is characterized in that,
Above-mentioned refrigerant is a carbon dioxide.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008004779U JP3145048U (en) | 2008-07-11 | 2008-07-11 | Electric expansion valve and refrigeration cycle |
| JP2008004779 | 2008-07-11 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201327255Y true CN201327255Y (en) | 2009-10-14 |
Family
ID=41179227
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008201343511U Expired - Lifetime CN201327255Y (en) | 2008-07-11 | 2008-09-25 | Electric expansion valve and refrigeration circulation system |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3145048U (en) |
| CN (1) | CN201327255Y (en) |
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