WO2021066356A1

WO2021066356A1 - Electronic expansion-and-redirection integrated valve

Info

Publication number: WO2021066356A1
Application number: PCT/KR2020/012501
Authority: WO
Inventors: 박장식; 홍태호; 박지완; 이찬얼
Original assignee: 동일기계공업 주식회사; 동일테크윈 주식회사
Priority date: 2019-10-02
Filing date: 2020-09-16
Publication date: 2021-04-08
Also published as: KR102447040B1; KR20210040227A

Abstract

The present invention relates to an electronic expansion-and-redirection integrated valve. More particularly, the present invention provides an expansion valve capable of switching not only to a closed state in which the flow of a refrigerant is blocked, but also to an expansion state in which an expansion gap is formed so as to expand the refrigerant or to a fully open state in which the refrigerant is circulated without being expanded. The expansion valve comprises: a valve body (100) having a block shape and having a channel (110) formed therein such that an input port (101) and an output port (102) communicate with each other; a rotary valve (200) provided to be able to rotate in the circumferential direction inside the channel (110), the rotary valve (200) having an expansion recess (210) and a channel hole (220) formed therein; a valve plate (300) having a through-hole (310) formed therein; an airtight member (400) made of an elastic airtight material and integrally provided on at least one surface of the rotary valve (200) to be able to rotate toward the valve plate (300), thereby securing airtightness between the through-hole (310) of the valve plate (300) and the rotary valve (200); and a driving member (500) for delivering rotary power to the rotary valve (200). Accordingly, precise control is enabled while simplifying the configuration of a vehicle air conditioner. Particularly, airtightness regarding the refrigerant, and processability and productivity regarding the product are improved, thereby lowering the product production cost and maximizing market competitiveness.

Description

Electronic expansion and direction change integrated valve

The present invention relates to an integrated electronic expansion and direction change valve, in particular, in a closed state to block the flow of refrigerant, as well as an expanded state in which the refrigerant is expanded by forming an expansion gap, or in a fully open state in which the refrigerant is circulated without expansion. It is to provide an expansion valve that can be switched between degrees and simplifies the configuration of the vehicle air conditioner, enables precise control, and increases the airtightness of the refrigerant and the processability and productivity of the product, thereby lowering the production cost of the product while lowering the market competitiveness. It relates to a device that can maximize the.

In general, a refrigeration cycle includes a compressor, a condenser, an expansion valve, and an evaporator, and is widely used for cooling a refrigerator or an air conditioner for cooling by circulating a refrigerant.

Here, the expansion valve constituting the refrigeration cycle is a valve that reduces the high-temperature and high-pressure liquid refrigerant condensed and liquefied in the condenser to a pressure that can cause evaporation by throttling action, and an appropriate amount of refrigerant to absorb sufficient heat from the evaporator. It plays a role of regulating supply.

However, the conventional expansion valve has a problem in that the configuration is complicated and precise control is difficult, and in particular, not only the processability and productivity are poor, but also the airtightness to the refrigerant is low.

Recently, the refrigeration cycle has been improved to construct a heat pump that circulates the refrigerant in the reverse direction, and thus it is used as a heat source such as a heating cabinet or a heating air conditioner.

According to the configuration of such a heat pump, the expansion valve for cooling and the expansion valve for heating were conventionally configured respectively, but in this case, there was a problem that not only the manufacturing cost increased, but also the circulation line of the refrigerant became complicated and control was difficult. .

Accordingly, a two-way expansion valve that expands while passing the refrigerant in both forward and reverse directions, and a three-way expansion valve that expands while passing the refrigerant through one of two output ports from one input port have been developed.

Patent Document 1, Korean Patent Publication No. 2011-0043128, Patent Document 2, Domestic Patent Publication No. 10-0835259, and Patent Document 3, Korean Patent Publication No. 10-0432158, have two from one input port. A technique of expanding the refrigerant while switching the refrigerant to any of the above output ports is disclosed.

However, the conventional expansion valve disclosed in Patent Literature 1 to Patent Literature 3 is only focused on communicating any one of two or more output ports from one input port, and forms an expansion gap of an appropriate size to save the refrigerant. There is a problem in the prior art that it cannot be adjusted to an expanded state to expand and a fully open state to pass the refrigerant as it is without expanding.

The present invention is to solve the above problems, simplifies the configuration of a vehicle air conditioner, enables precise control, and increases the airtightness of the refrigerant and the workability and productivity of the product, thereby lowering the production cost of the product and enhancing market competitiveness. We intend to provide an integrated electronic expansion and direction change valve that can be maximized.

The electronic expansion and direction change integrated valve according to the present invention has a block shape, and includes an input port through which refrigerant is supplied to one side, an output port through which refrigerant is discharged to the other side, and a flow path that communicates the input port and the output port. A valve body formed therein; Made in a plate shape, provided to be rotatable in a circumferential direction in the flow path between the input port and the output port, an expansion recess extending in a circumferential direction with a predetermined radial width, and an end of the expansion recess A rotary valve in communication with a flow path hole having a radial width greater than that of the expansion recess; A valve plate formed in a plate shape, stacked and arranged to contact the rotary valve, fixed non-rotatably in the flow path of the valve body, and having a through hole formed in a circumferential direction; An airtight member made of synthetic resin or an elastic airtight material and provided so as to be integrally rotatable on at least one surface of the rotary valve toward the valve plate to secure airtightness between the through hole of the valve plate and the rotary valve; It is achieved by including a drive member for transmitting a rotational force to the rotational valve.

In this case, it is preferable that the expansion recesses overlap along the circumferential direction from the outer side in the radial direction of the through hole to form an expansion gap.

Further, the output ports of the valve body include a first output port and a second output port independently formed from each other; The through-holes of the valve plate include first through-holes and second through-holes spaced apart from each other in a circumferential direction corresponding to the first output port and the second output port, respectively; It is preferable that the refrigerant can be supplied by switching from one input port to one of the two output ports.

In addition, it is preferable that the airtight member and the rotary valve have a polygonal shape or an arc shape that engages and engages with each other in contact with each other, so that the airtight member rotates integrally when the rotary valve is rotated.

In particular, the driving member includes a shaft connected to the rotation center of the rotation valve and integrally rotating, and a step motor capable of controlling a rotation angle according to power control and transmitting rotational force to the shaft; It is preferable that the valve plate has a support groove rotatably supporting the lower end of the shaft at the center.

The present invention as described above enables precise control while simplifying the configuration of an air conditioner for a vehicle, and in particular, it is an invention capable of maximizing market competitiveness while lowering the production cost of the product by increasing the airtightness of the refrigerant and the workability and productivity of the product. .

1 is a front cross-sectional view showing an example of an integrated electronic expansion and direction change valve according to the present invention,

2 is a plan view showing a rotary valve, an airtight member, and a valve plate in an example of an integrated electronic expansion and direction change valve according to the present invention;

3 is a view showing a state in which a rotary valve and an airtight member are integrated with each other in an example of the electronic expansion and direction change integrated valve according to the present invention.

4 is a plan view showing a state in which a rotary valve, an airtight member, and a valve plate are stacked in an example of an integrated electronic expansion and direction change valve according to the present invention;

5 is an exploded perspective view of a rotating valve, an airtight member, and a valve plate in an example of an integrated electronic expansion and direction change valve according to the present invention;

6 is a bottom exploded perspective view of a rotary valve, an airtight member, and a valve plate in an example of an integrated electronic expansion and direction change valve according to the present invention;

7 is a diagram illustrating an expansion gap formed according to a radial position of an expansion recess in an example of an integrated electronic expansion and direction change valve according to the present invention;

8 is a diagram showing a closed state of an output port in an example of an integrated electronic expansion and direction change valve according to the present invention;

9 is a diagram showing an expansion state of a refrigerant with respect to an output port in an example of an integrated electronic expansion and direction change valve according to the present invention;

10 is a diagram showing a fully open state of a refrigerant to an output port in an example of an integrated electronic expansion and direction change valve according to the present invention;

11 is a front cross-sectional view showing another example of an integrated electronic expansion and direction change valve according to the present invention;

12 is a view showing the lower body of the valve body in another example of the integrated electronic expansion and direction change valve according to the present invention.

13 is a plan view showing a valve plate in another example of an integrated electronic expansion and direction change valve according to the present invention;

14 is a plan view showing a state in which a rotary valve, an airtight member, and a valve plate are stacked in another example of the integrated electronic expansion and direction change valve according to the present invention;

15 is an exploded perspective view of a rotating valve, an airtight member, and a valve plate in another example of an integrated electronic expansion and direction change valve according to the present invention;

16 is a bottom exploded perspective view of a rotary valve, an airtight member, and a valve plate in another example of an integrated electronic expansion and direction change valve according to the present invention;

17 is a perspective view showing a bush in another example of an integrated electronic expansion and direction change valve according to the present invention;

18 is a view showing a closed state of both the first output port and the second output port in another example of the integrated electronic expansion and direction change valve according to the present invention.

19 is a diagram showing an expanded state of a refrigerant with respect to a first output port and a closed state of a second output port in another example of the integrated electronic expansion and direction change valve according to the present invention;

FIG. 20 is a diagram illustrating a fully open state of a refrigerant with respect to a first output port and a closed state of a second output port in another example of the integrated electronic expansion and direction change valve according to the present invention.

21 is a view showing a closed state of both the first output port and the second output port in another example of the integrated electronic expansion and direction change valve according to the present invention.

22 is a diagram showing a closed state of a first output port and an expanded state of a refrigerant with respect to a second output port in another example of the integrated electronic expansion and direction change valve according to the present invention;

23 is a view showing a closed state of a first output port and a completely open state of a refrigerant to a second output port in another example of the integrated electronic expansion and direction change valve according to the present invention.

[Explanation of code]

100: valve body 101: input port

102: output port 102a: first output port

102b: second output port 104: sealing

106: fastening ring 110: euro

120: main body 130: lower body

140: fixed body 141: stepped portion

150: cover 151: fastening means

160: main sealing 200: rotary valve

201: coupling hole 210: expansion recess

220: flow path 230: valve body

300: valve plate 301: support groove

310: through hole 311: first through hole

312: second through hole 400: airtight member

500: drive member 510: shaft

511: shaft gear 520: step motor

521: output shaft gear 530: reduction gear

600: bush 610: boss

620: wing w: radial width of the expansion recess

W: radial width of the open hole

1 is a front cross-sectional view showing an example of an electronic expansion and direction change integrated valve according to the present invention, and FIG. 2 is a rotary valve, an airtight member, and a valve plate in an example of the electronic expansion and direction change integrated valve according to the present invention. As a plan view showing, Fig. 2(a) shows a rotary valve, Fig. 2(b) shows an airtight member, and Fig. 2(c) shows a valve plate, respectively.

And, Figure 3 is a diagram showing a state in which the rotary valve and the airtight member are integrated with each other in an example of the integrated electronic expansion and direction change valve according to the present invention, Figure 3 (a) is a perspective view, ( b) is a bottom perspective view, and FIG. 4 is a plan view showing a state in which a rotary valve, an airtight member, and a valve plate are stacked in an example of the electronic expansion and direction change integrated valve according to the present invention.

In addition, FIG. 5 is an exploded perspective view of a rotating valve, an airtight member, and a valve plate in an example of an integrated electronic expansion and direction change valve according to the present invention, and FIG. 6 is an exploded perspective view of the integrated electronic expansion and direction change valve according to the present invention. In one example, it is an exploded perspective view of the bottom of the rotary valve, the airtight member, and the valve plate, and FIG. 7 is an expansion gap formed according to the radial position of the expansion recess in an example of the integrated electronic expansion and direction change valve according to the present invention. It is a diagram explaining.

In addition, FIG. 8 is a view showing a closed state of an output port in an example of an integrated electronic expansion and direction change valve according to the present invention, and FIG. 9 is an output port in an example of an integrated electronic expansion and direction change valve according to the present invention. FIG. 10 is a diagram showing an expanded state of the refrigerant to and FIG. 10 is a diagram illustrating a fully opened state of the refrigerant to an output port in an example of an integrated electronic expansion and direction change valve according to the present invention.

In this case, in Figs. 8 to 10, each (a) is a plan view, and (b) is a cross-sectional view taken along lines B-B to D-D shown in Fig. (a).

Next, FIG. 11 is a front cross-sectional view showing another example of the electronic expansion and direction change integrated valve according to the present invention, and FIG. 12 is a lower portion of the valve body in another example of the electronic expansion and direction change integrated valve according to the present invention. As a diagram showing the body, Figure 12 (a) is a plan view, Figure 12 (b) is a cross-sectional view taken along line AA of Figure 12 (a), Figure 13 is an integrated electronic expansion and direction change according to the present invention It is a plan view showing a valve plate in another example of a valve.

14 is a plan view showing a state in which a rotary valve, an airtight member, and a valve plate are stacked in another example of the electronic expansion and direction change integrated valve according to the present invention, and FIG. 15 is an electronic expansion and direction change integrated valve according to the present invention. An exploded perspective view of a rotary valve, an airtight member, and a valve plate in another example of a direction change integrated valve, and FIG. 16 is a rotary valve, an airtight member, and in another example of the electronic expansion and direction change integrated valve according to the present invention. It is an exploded perspective view of the bottom of the valve plate.

In addition, Fig. 17 is a perspective view showing a bush in another example of an integrated electronic expansion and direction change valve according to the present invention.

In addition, FIG. 18 is a diagram showing a closed state of both the first output port and the second output port in another example of the electronic expansion and direction change integrated valve according to the present invention, and FIG. 19 is an electronic expansion and direction according to the present invention. In another example of the integrated switching valve, a diagram showing the expanded state of the refrigerant with respect to the first output port and the closed state of the second output port, and FIG. 20 is a diagram showing another example of the electronic expansion and direction switching integrated valve according to the present invention. It is a diagram showing a state in which the refrigerant is completely open to the first output port and a state in which the second output port is closed.

And, FIG. 21 is a diagram showing a closed state of both the first output port and the second output port in another example of the electronic expansion and direction change integrated valve according to the present invention, and FIG. 22 is an electronic expansion and direction according to the present invention. In another example of the integrated switching valve, a diagram showing a closed state of the first output port and an expanded state of the refrigerant with respect to the second output port, and FIG. 23 is a diagram showing another example of the electronic expansion and direction switching integrated valve according to the present invention. A diagram showing a closed state of the first output port and a completely open state of the refrigerant to the second output port.

At this time, in FIGS. 18 to 23, each (a) is a plan view, and (b) is a cross-sectional view taken along lines E-E to J-J shown in each (a).

The electronic expansion and direction change integrated valve according to the present invention simplifies the configuration of the vehicle air conditioner and enables precise control, and in particular, increases the airtightness of the refrigerant and the processability and productivity of the product, thereby lowering the production cost of the product and enhancing market competitiveness. What can be maximized is the basic feature of the technology.

An embodiment of the present invention will be described in detail with reference to the accompanying drawings as follows.

The present invention is an integrated valve for electronic expansion and direction change through which the refrigerant passes when the refrigerant is circulated for cooling in a vehicle air conditioner, and may be provided between the condenser and the evaporator.

First, an example of the electronic expansion and direction change integrated valve according to the present invention is made of a block shape, as shown in Figs. 1 to 10, an input port 101 for supplying a refrigerant to one side, and a refrigerant to the other side. A valve body 100 having an output port 102 discharged and a flow path 110 communicating the input port 101 and the output port 102 therein; Made of a plate shape, provided to be rotatable in the circumferential direction within the flow path 110 between the input port 101 and the output port 102, and extends along the circumferential direction with a predetermined radial width (w) The expansion recess 210 is connected to the end of the expansion recess 210, the flow path hole 220 having a radial width (W) wider than the radial width (w) of the expansion recess (210) The rotary valve 200 is formed; A valve plate in which a through hole 310 is formed in a circumferential direction, which is formed in a plate shape, is stacked and disposed to contact the rotary valve 200, and is fixed to be non-rotatably in the flow path 110 of the valve body 100. 300) and; It is made of synthetic resin or an elastic airtight material and is integrally rotatably provided on at least one surface of the rotation valve 200 toward the valve plate 300, and the through hole 310 of the valve plate 300 and the rotation valve 200 ) And an airtight member 400 for securing airtightness between them; It is preferable to include a driving member 500 for transmitting a rotational force to the rotation valve 200.

That is, an example of the electronic expansion and direction change integrated valve of the present invention basically includes a valve body 100, a rotary valve 200, a valve plate 300, an airtight member 400, and a driving member 500. I'm doing it.

First, the valve body 100 is a structure constituting the basic skeleton in the integrated electronic expansion and direction change valve of the present invention, and is made of a block shape, preferably a substantially hexahedral block shape.

At this time, there will be no limitation on the external shape of the valve body 100, and may be a polygonal column or a cylindrical shape, including a square column of a hexahedron.

In such a valve body 100, as shown in FIG. 1, an input port 101 to which a refrigerant is supplied may be formed on one side, that is, on the upper side in the drawing, and on the other side of the valve body 100, that is, on the lower side in the drawing. An output port 102 through which the refrigerant is discharged may be formed.

In addition, a flow path 110 for communicating the input port 101 and the output port 102 into one is formed in the valve body 100, so that the refrigerant flows through the flow path 110 to the input port. It can pass from 101 to the output port 102.

Accordingly, for example, when cooling is driven, the refrigerant entering the input port 101 may be discharged to the output port 102.

For convenience of explanation, the input port 101 is formed on the upper side of the valve body 100 and the output port 102 is formed on the lower side, and is described below, but each port according to the arrangement direction of the valve body 100 It will be apparent that the location of is subject to change and is not limited thereto.

In the middle of the flow path 110 of the valve body 100, a rotary valve 200 and a valve plate 300 for controlling passage and expansion of the refrigerant may be provided.

Here, when the above-described valve body 100 is described in more detail, the valve body 100 may be formed of a single body, but is divided into a plurality of bodies as shown in FIG. 1 in consideration of formability and assembly properties. So it can be made.

For example, the valve body 100 may be manufactured by being divided into a main body 120, a lower body 130, and a fixed body 140, and then assembled into one.

First, the main body 120 is located at the center of the valve body 100 and has a flow path 110 penetrating through it, and the rotary valve 200 and the airtight member 400 and the valve plate to be described below. 300 may be provided on the inner circumferential surface of the main body 120.

At this time, the inner circumferential surface of the main body 120 is processed to a uniform inner diameter without a step, so that it is possible to increase workability.

In addition, the input port 101 and the output port 102 are formed in the lower body 130, and the main body 120 described above as shown in FIG. 1 is disposed in the inner center of the lower body 130. It can be.

In addition, as shown in FIG. 1, the fixed body 140 may be assembled by maintaining airtightness in the upper opening of the lower body 130.

According to this configuration, in the valve body 100, the flow path 110 from the input port 101 to the output port 102 by the main body 120, the lower body 130, and the fixed body 140 ) May be formed.

In Figure 1, reference numeral 104 is a sealing, located between the main body 120 and the lower body 130 to prevent the leakage of the refrigerant, and located between the fixed body 140 and the lower body 130 to prevent the refrigerant It will be able to prevent the leakage of.

In this case, the driving member 500 to be described later may be provided through the fixed body 140.

Next, the rotary valve 200 is a disk made of a plate material having a predetermined thickness, as shown in Figs. 2 to 6, and between the input port 101 and the output port 102 It is disposed in the flow path 110 so as to cross the flow path 110 and is provided to be rotatable in the circumferential direction.

As described above, the rotary valve 200 may be provided on the inner circumferential surface of the main body 120 in the valve body 100.

At this time, the rotation valve 200 is rotated to have an outer diameter slightly smaller than the inner diameter of the main body 120 so that the valve body 100 can smoothly rotate within the inner circumferential surface of the main body 120 The valve 200 is formed.

As shown in FIG. 2, the rotary valve 200 has an expansion recess 210 and a flow path hole 220 formed along the circumferential direction.

First, the expansion recess 210 is formed in a shape extending along the circumferential direction with a predetermined radial width w, and the flow path hole 220 is communicated with the end of the expansion recess 210 It has a radial width (W) wider than the radial width (w) of the expansion recess 210 and is formed in a shape extending along the circumferential direction.

At this time, the forming position of the expansion recess 210 may be located within the radial width W of the flow path hole 220 so that the expansion recess 210 and the flow path hole 220 communicate with each other, It may be located at the center side or outside the flow path hole 220 out of the radial width (W).

However, the preferred position of the expansion recess 210 for effectively performing the expansion of the refrigerant will be described later. First, the expansion recess 210 is located outside the radial direction of the rotary valve 200 so that the expansion recess An example in which the 210 and the flow path hole 220 are formed in communication will be described below.

In addition, in the rotary valve 200, the expansion recess 210 overlaps the through hole 310 of the valve plate 300 to be described later to form an expansion gap, thereby expanding the refrigerant.

In addition, in the rotary valve 200, the flow path hole 220 overlaps the through hole 310 so as to pass the refrigerant as it is without expansion of the refrigerant.

Here, the rotation direction of the rotation valve 200 may be controlled in both clockwise and counterclockwise directions in FIG. 2A, but in consideration of control precision, the rotation valve 200 is in one direction, For example, it would be desirable to control it to rotate only counterclockwise.

If the rotation valve 200 is controlled to rotate only in the counterclockwise direction, as illustrated in FIG. 2A, the expansion recess 210 and the flow path hole 220 are expanded. It is preferable that the flow path hole 220 is positioned on the clockwise side with respect to the recess 210.

That is, when the rotary valve 200 rotates in a counterclockwise direction, the expansion recess 210 overlaps the through hole 310 before the flow path hole 220, so that the refrigerant expands beforehand, and then the rotary valve ( When 200 is further rotated, it would be better to allow the flow path hole 220 to overlap the through hole 310 so that the refrigerant can be completely opened.

In addition, as shown in FIG. 1, the rotary valve 200 is stacked and disposed so that the valve plate 300 abuts and contacts, and in particular, the valve plate 300 is stacked and disposed to abut and contact the lower side of the rotary valve 200. will be.

At this time, as described above, the rotary valve 200 is provided so as to be rotatable in the circumferential direction within the valve body 100, while the valve plate 300 is fixedly installed in the valve body 100 so as not to be rotatable.

As such, the valve plate 300 is made of a plate material, and the outer circumferential shape of the valve body 100 may be manufactured in a polygonal shape in order to prevent rotation within the valve body 100.

However, after making the valve plate 300 in the form of a disk in consideration of formability and assembling property, a cutout (not shown) partially cut off is formed on the outer periphery, and together with this, the valve body 100 It is preferable that a protrusion (not shown) corresponding to this cutout is formed in the valve body 100 so that the valve plate 300 is non-rotatably assembled into the valve body 100.

Accordingly, the valve plate 300 is limited in rotation in the circumferential direction in a state assembled to the valve body 100, and a refrigerant between the outer circumferential surface of the valve plate 300 and the inner circumferential surface of the main body 120 Airtightness must be maintained to prevent leakage of the product.

At this time, the valve plate 300 has a predetermined radial width and extends along the circumferential direction as shown in FIG. 2(c), and a fan-shaped through hole 310 with a roughly cut off center is formed. .

In particular, the shape of the through hole 310 may be manufactured to have substantially the same shape as the flow path hole 220 of the rotary valve 200 described above, but the cross-sectional area of the through hole 310 is the flow path hole 220 and A similar or slightly wider one would be better.

In this case, in the case where the cross-sectional area of the through hole 310 is to be slightly wider than the flow path hole 220, the radial width is kept similar, while the circumferential width is greater than the flow path hole 220. 310) should be formed somewhat wider.

In the rotary valve 200 described above, the radial position where the expansion recess 210 is formed and the circumferential width of the through hole 310 affect the control precision of the electronic expansion and direction change integrated valve according to the present invention. This will be described later.

According to this configuration, the rotary valve 200 can control whether or not the refrigerant expands as well as the opening and closing of the expansion valve according to the present invention by a relative rotational motion with the valve plate 300 fixed in the valve body 100. There is.

For example, when the expansion recess 210 of the rotary valve 200 described above overlaps with the through hole 310 of the valve plate 300 as shown in FIG. 9, an expansion gap is formed to allow the refrigerant to expand. Will be.

In addition, when the rotary valve 200 further rotates counterclockwise so that the flow path 220 overlaps the through hole 310 of the valve plate 300 as shown in FIG. 10, the flow path of the refrigerant is secured wider. It will be fully open without expansion of the refrigerant.

In addition, as shown in FIG. 8, when neither of the expansion recess 210 or the flow path hole 220 of the rotary valve 200 overlaps the through hole 310 of the valve plate 300, the expansion valve is in a closed state. The flow of refrigerant will be blocked.

In particular, in the present invention, in order to more reliably prevent leakage of refrigerant in such a closed state, an airtight member 400 is additionally provided on at least one surface of the rotary valve 200.

The airtight member 400 is made of an elastic airtight material such as synthetic resin, Teflon, rubber, or silicone, and is provided to be integrally rotatable with the rotary valve 200 toward the valve plate 300.

At this time, the airtight member 400 may be manufactured separately from the rotary valve 200 and then integrated through adhesion, or the airtight member 400 and the rotary valve 200 are integrated through insert injection, etc. It could also be molded and manufactured.

In particular, since the airtight member 400 functions only when the rotary valve 200 completely closes the through hole 310 of the valve plate 300, the above-described The airtight member 400 will not need to be provided.

That is, the valve body 230 located inside the expansion recess 210 in which the refrigerant expands by forming a fine gap with the through hole 310 of the valve plate 300 in the rotary valve 200 There will be no need for the hermetic member 400 to be provided.

However, in order to completely close the through hole 310 of the valve plate 300, the airtight member 400 may be formed in all portions of the rotary valve 200 except for the valve body 230, The airtight member 400 closes the through hole 310 of the valve plate 300 to maintain high airtightness.

To this end, as illustrated in FIGS. 3 to 6, an airtight member 400 may be provided on the lower side of the rotary valve 200 in contact with the valve plate 300, and to expand the refrigerant. The airtight member 400 is provided in portions other than the valve body 230.

There will be no limit to the thickness of the airtight member 400, and the airtight member 400 corresponding to the thickness of half of the rotary valve 200 is illustrated in the drawings.

Accordingly, when the airtight member 400 is adhered to the rotary valve 200 without insert injection, the rotary valve 200 may be formed in advance in the shape of the airtight member 400 as illustrated in FIG. 6. Correspondingly, it will need to be engraved.

According to this configuration, when the rotary valve 200 closes the through hole 310 of the valve plate 300, the airtight member 400 is positioned at a portion corresponding to the through hole 310, thereby refrigerant It becomes possible to effectively prevent the leakage of.

Finally, the driving member 500 may include a motor as a driving source for transmitting the rotational force to the rotation valve 200 described above.

First, as shown in FIG. 1, the driving member 500 has a shaft 510 connected to the rotation center of the rotation valve 200 to rotate integrally, and the rotation angle can be controlled according to power control. It may include a step motor 520 that transmits the rotational force to the shaft 510.

In addition, the rotational force output to the output shaft of the step motor 520 is transmitted to the shaft 510 directly as shown in FIG. 1 or indirectly as shown in FIG. 11, although it will be described in another example below in order to rotate the shaft 510 It will be possible.

Here, when the rotational force of the step motor 520 is directly transmitted to the shaft 510, the output shaft of the step motor 520 may be integrally configured with the shaft 510 as shown in FIG. 1.

In this case, the rotational speed of the output shaft with respect to the step motor 520 will be directly transmitted to the shaft 510 without a separate deceleration.

In addition, the shaft 510 is disposed so that a part of the shaft 510 passes through the flow path 110 of the valve body 100 described above, and the valve plate 300 and the airtight member 400 from the bottom of the shaft 510 And, the rotary valve 200 will be sequentially stacked and positioned.

In addition, the valve plate 300 is not affected by the rotation of the shaft 510, and only the rotation center is supported by the shaft 510, and the shaft 510 is It is placed in an idle state.

However, the rotation valve 200 has a protrusion as shown in FIGS. 2 to 6 in the coupling hole 201 formed in the center of the rotation valve 200 so that it can rotate integrally with the shaft 510 as described above. Protrusion is formed, and a cutout (not shown) is formed in the shaft 510 to correspond to the protrusion of the coupling hole 201 described above, so that the protrusion of the coupling hole 201 and the cutout of the shaft 510 are Are interlocked.

Accordingly, since the shaft 510 and the rotary valve 200 can rotate integrally, it is possible to transmit the rotational force of the shaft 510 to the rotary valve 200.

Until now, a structure in which the rotary valve 200 is stacked on the valve plate 300 has been described, but although not shown, a structure in which the valve plate 300 is stacked on the rotary valve 200 may be used as necessary, and two valves A structure in which the rotary valve 200 is positioned between the plates 300 may be good.

In this case, the airtight member 400 may be provided on the upper side or both upper and lower sides of the rotary valve 200, and in the case of a structure in which the rotary valve 200 is positioned between the two valve plates 300, leakage of refrigerant It will be most effective in preventing it.

Additionally, as shown in FIG. 1, it would be desirable to add a ring-shaped main sealing 160 along the periphery of the opening communicating with the output port 102 in the lower body 130.

The main sealing 160 is made of an airtight material having elasticity, and is provided between the valve plate 300 and the lower body 130, thereby distinguishing the input port 101 and the output port 102 from each other with high airtightness. do.

As a result, when the refrigerant is shut off from the input port 101 to the output port 102 in the valve body 100 by the control of the rotary valve 200 described above, leakage of the refrigerant can be effectively prevented.

Until now, the operation of simply forming the expansion recess 210 and the flow path hole 220 to pass the refrigerant as it is without the expansion of the refrigerant or expansion of the refrigerant has been described. By appropriately defining the position, it is possible to increase the expansion efficiency of the refrigerant.

Here, the expansion efficiency means the degree of throttling, and the throttling means a valve, a cock, or a plate with a small hole attached to a part of the fluid passage to narrow the cross-sectional area of the flow. It is forcibly increased, and as a result, the distance between molecules increases and the pressure drops, which is a phenomenon.

In other words, it can be said that the higher the degree of throttling by forming an expansion gap of an appropriate size, the better the expansion efficiency.

For example, as shown in (a) of FIG. 7, the expansion recess 210 may be formed approximately in the middle of the radial direction of the rotary valve 200 to be formed in communication with the flow path hole 220, or As shown in (b), the expansion recess 210 may be formed at the radial center side of the rotary valve 200 to communicate with the flow path hole 220, or the expansion recess 210 may be formed as shown in FIG. 7(c). The recess 210 may be formed outside the rotary valve 200 in the radial direction to be formed in communication with the flow path hole 220.

First, as shown in (a) of FIG. 7, when the expansion recess 210 is formed approximately in the radial direction of the rotary valve 200 to communicate with the flow path hole 220, the expansion recess Regardless of the circumferential width of 210, the cross-sectional area connected to the through hole 310 formed in the valve plate 300 is determined according to the size of the radial width w of the expansion recess 210, and this cross-sectional area Will affect the expansion efficiency of the refrigerant.

In order to increase the expansion efficiency by properly maintaining this cross-sectional area, the end of the expansion recess 210 must be finely overlapped with the through hole 310 to form an expansion gap, so the rotary valve 200 More precise control is inevitably required to control the rotation angle of the machine.

In addition, as shown in (b) of FIG. 7, when the expansion recess 210 is formed at the radial center side of the rotary valve 200 to communicate with the flow path hole 220, the rotary valve It is not necessary to precisely control the rotation angle of (200).

However, since the circumferential width at which the expansion recess 210 of the rotary valve 200 and the through hole 310 of the valve plate 300 overlap is remarkably small, there is a limitation in forming a long expansion gap for the refrigerant. There is.

On the other hand, as shown in (c) of FIG. 7, when the expansion recess 210 is formed on the outer peripheral side in the radial direction of the rotary valve 200 to communicate with the flow path hole 220, the above-described As described above, there is no need to precisely control the rotation angle of the rotation valve 200, and the circumferential width at which the expansion recess 210 of the rotation valve 200 and the through hole 310 of the valve plate 300 overlap. By being able to secure relatively long, it becomes possible to form the expansion gap long as a result.

As a result, in the present invention, it is most preferable that the expansion recess 210 is overlapped along the circumferential direction from the outer side in the radial direction of the through hole 310 to form an expansion gap.

Next, it will be described to improve the coupling property of the rotary valve 200 and the hermetic member 400 described above.

That is, in the present invention, the airtight member 400 and the rotary valve 200 are formed in a polygonal shape or an arc shape to be engaged with each other in contact with each other, and the airtightness when the rotary valve 200 is rotated. It would be desirable to allow the member 400 to rotate integrally.

For example, as shown in Figs. 5 and 6, a convex convex portion is formed in an approximately square pillar shape near the center of the rotary valve 200, and the convex portion has a square pillar shape near the center of the airtight member 400. It is possible to form a concave concave portion corresponding to the concave portion, so that the concave portion and the convex portion engage with each other.

In addition, a convex convex portion is formed in a substantially hook-shaped arc shape near the center of the airtight member 400, and a concave convex portion is formed in the vicinity of the center of the rotary valve 200 to correspond to the convex portion. It is also possible to make the convex portions engage with each other.

As a result, it is possible to increase the coupling force between the rotary valve 200 and the airtight member 400, so that when the rotary valve 200 is rotated, the airtight member 400 molded by adhesion or insert injection is separated. It can be effectively prevented.

In addition, in the present invention, the driving member 500 has a shaft 510 connected to the rotation center of the rotation valve 200 and integrally rotating as described above, and a rotation angle control according to power control It is possible and includes a step motor 520 that transmits rotational force to the shaft 510; In particular, it is preferable that the valve plate 300 has a support groove 301 rotatably supporting the lower end of the shaft 510 in the center.

That is, a support groove 301 is formed in the center of the valve plate 300 as shown in FIG. 5, and the support groove 301 of the valve plate 300 is rotatable at the lower end of the shaft 510 as shown in FIG. By being supported, it is possible to reliably prevent eccentricity with respect to the shaft 510.

In addition, the lower end of the shaft 510 pushes the valve plate 300 downward, so that the bottom surface of the valve plate 300 presses the main sealing 160 located at the lower side thereof, so that the valve plate 300 and the main It becomes possible to ensure a higher airtightness between the sealing (160).

Next, another example of the electronic expansion and direction change integrated valve according to the present invention will be described with reference to FIGS. 11 to 20.

Another example of the electronic expansion and direction change integrated valve of the present invention, the output port 102 of the valve body 100 includes a first output port (102a) and a second output port (102b) formed independently of each other, ; The through hole 310 of the valve plate 300 corresponds to the first output port 102a) and the second output port 102b, respectively, and a first through hole 311 and a first through hole 311 spaced apart from each other in the circumferential direction. Including 2 through holes 312; It is characterized in that the refrigerant can be supplied by switching from one input port 101 to one of the two output ports 102a and 102b.

That is, in another example of the electronic expansion and direction change integrated valve of the present invention, two output ports 102a and 102b are formed in the valve body 100 in order to circulate the refrigerant through different paths during cooling and heating. And, two through

holes

311 and 312 are formed in the valve plate 300.

Accordingly, another example of the electronic expansion and direction change integrated valve of the present invention is for application to a heat pump of an air conditioner for a vehicle, particularly for an electric vehicle, both of the forward circulation of the refrigerant for cooling and the reverse circulation of the refrigerant for heating. As one electromagnetic valve through which the refrigerant passes, it may be provided between the condenser and the evaporator.

Description of the same configuration and operation as an example of the electronic expansion and direction change integrated valve according to the present invention described above will be omitted.

First, as shown in FIGS. 11 and 12, a first output port 102a) and a second output port 102b through which refrigerant is discharged are formed on the left and right sides of the valve body 100 to face each other.

In addition, a flow path 110 for communicating the input port 101, the first output port 102a, and the second output port 102b into one is formed in the valve body 100. , Through this flow path 110, the refrigerant may pass from the input port 101 to the first output port 102a) or the second output port 102b.

Accordingly, for example, during cooling, the refrigerant entering the input port 101 will be discharged to the first output port 102a, and during heating, the refrigerant entering the input port 101 is discharged to the second output port 102b. ), etc. will be possible.

For convenience of explanation, the input port 101 is formed on the upper side of the valve body 100, and the first output port 102a) and the second output port 102b are formed on the lower side, and the valve It will be apparent that the position of each port may be changed according to the arrangement direction of the body 100, and is not limited thereto.

In addition, as shown in FIG. 12, the lower body 130 has the above-described input port 101, a first output port 102a), and a second output port 102b, and the lower body 130 The main body 120 described above as shown in FIG. 11 may be disposed in the inner center of ).

At this time, as shown in FIG. 12, the first output port 102a) and the second output port 102b are disposed to face each other on the left and right sides of the drawing at substantially equal heights, and the input port 101 The first output port 102a) and the second output port 102b may be formed at a right angle, but with a height difference.

However, in FIG. 11, for convenience of explanation, it is illustrated that the input port 101 is formed in the same direction as the second output port 102b (left side in the drawing) but with a height difference, but in reality, as shown in FIG. 12, the input port 101 (101) is preferably formed in a direction perpendicular to both the first output port (102a) and the second output port (102b), which is a mistake when connecting the refrigerant pipe to the expansion valve according to the present invention. It will play a role in preventing assembly and increasing design freedom for the heat pump.

Next, the rotary valve 200 is in the flow path 110 so as to cross the flow path 110 between the input port 101 and the first output port 102a and the second output port 102b. It is arranged and provided to be rotatable in the circumferential direction.

At this time, in the rotary valve 200, the expansion recess 210 is overlapped with the first through hole 311 or the second through hole 312 of the valve plate 300 to form an expansion gap, thereby expanding the refrigerant. , The flow path hole 220 is overlapped with the first through hole 311 or the second through hole 312 so as to pass the refrigerant as it is without expansion of the refrigerant.

In addition, the valve plate 300 has a first through hole 311 and a second through hole 312 spaced apart along the circumferential direction as shown in FIG. 13, and preferably, a phase angle difference of approximately 180 degrees. A first through hole 311 and a second through hole 312 are formed so as to be symmetrical with each other.

Here, the first through hole 311 corresponds to the first output port 102a formed in the lower body 130 of the valve body 100 as shown in FIG. 11, and the second through hole 312 Is corresponding to the second output port (102b) formed on the lower body (130) of the valve body (100).

In addition, the first through hole 311 and the second through hole 312 are preferably formed to have the same shape and cross-sectional area as shown in FIGS. 13 to 16.

According to this configuration, the rotary valve 200 controls the opening and closing of the expansion valve according to the present invention by a relative rotational motion with the valve plate 300 fixed in the valve body 100, so as to control whether the refrigerant is expanded or not. It is also possible to control the refrigerant flow path switching.

In addition, in another example of the electronic expansion and direction change integrated valve of the present invention, as shown in FIG. 11, a cover 150 is additionally provided on the upper side of the valve body 100.

The cover 150 is assembled on the upper side by wrapping the upper portion of the lower body 130 in the valve body 100 described above, and in particular, the driving member 500 may be provided on the cover 150.

The cover 150 may be assembled to surround the upper end of the lower body 130 by a plurality of fastening means 151.

In another example of the integrated electronic expansion and direction change valve according to the present invention, the rotational force of the step motor 520 is indirectly transmitted to the shaft 510, and the output shaft and the shaft of the step motor 520 as shown in FIG. Between 510, for example, a reduction gear 530 may be additionally disposed.

When the reduction gear 530 is applied as described above, as shown in FIG. 11, the reduction gear 530 is a two-stage gear having a separate rotation shaft and having a large diameter portion having a large outer diameter and a small diameter portion having a small outer diameter.

The rotation shaft for rotatably supporting the reduction gear 530 may be provided in a peripheral configuration such as the cover 150 or the fixed body 140, and in FIG. 11, the rotation shaft of the reduction gear 530 is the cover 150 An example that is supported by is shown.

At this time, the large diameter portion of the reduction gear 530 is engaged with the output shaft gear 521 fixed to the output shaft of the step motor 520, and the small diameter portion of the reduction gear 530 is fixed to the shaft 510. It is engaged with the shaft gear 511.

Accordingly, after the rotational force of the step motor 520 is reduced by the reduction gear 530, it can be transmitted to the shaft 510, and a high torque can be exhibited.

In addition, it is preferable that a bush 600 is provided in the middle of the shaft 510 to increase the adhesion between the rotary valve 200 and the valve plate 300 as shown in FIG. 11.

The bush 600 may be provided in the middle of the shaft 510 so that the above-described rotary valve 200 applies a force downward toward the valve plate 300.

To this end, the bush 600 may be fixed to the shaft 510 by a separate fastening means.

However, rather than this, the bush 600 is composed of a boss 610 through which the shaft 510 passes in the center as shown in FIG. 17, and a plurality of fan-shaped blades 620 extending radially from the boss 610. The valve body 100 is divided into a plurality of bodies, and one of the divided bodies is most preferably supporting the edge of the wing 620 of the bush 600 downward.

That is, the edge of the blade 620 of the bush 600 is positioned inside the inner circumferential surface of the main body 120 described above as shown in FIG. 11, and the fixed body 140 of the valve body 100 includes the bush 600 ) Is formed to protrude a stepped portion 141 for supporting downwardly of the wing 620.

Accordingly, as the fixed body 140 is placed on the lower body 130 and fastened with the fastening ring 106 to be screwed, the fixed body 140 is assembled downward, and as a result, the fixed body ( The stepped portion 141 of the 140) supports the edge of the wing 620 of the bush 600 downward.

According to this configuration, it is possible to increase the adhesion between the rotary valve 200 and the valve plate 300 more effectively, thereby effectively preventing the leakage of the refrigerant.

Hereinafter, the operation of another example of the electronic expansion and direction change integrated valve according to the present invention will be described in detail with reference to the drawings.

For example, when the air conditioner of a vehicle, more preferably an electric vehicle, cools, the refrigerant flows into the input port 101 in the valve body 100, and the refrigerant is discharged through the first output port 102a. I will be able to.

In addition, during heating, the refrigerant flowing from the valve body 100 to the input port 101 may be discharged through the second output port 102b.

At this time, the air conditioning controller of the electric vehicle sends an appropriate power or electrical signal to the step motor 520 to rotate the output shaft of the step motor 520 at a desired angle, and accordingly, the output shaft of the step motor 520 is The rotary valve 200 is rotated on the valve plate 300.

This action will be described in detail by dividing it according to the rotation angle of the rotation valve 200 as follows.

First, when the rotary valve 200 is rotated by the step motor 520 of the driving member 500 and the rotary valve 200 is positioned as shown in FIG. 18, the expansion recess of the rotary valve 200 ( Both the 210 and the flow path 220 are in a closed state that does not overlap with either the first through hole 311 and the second through hole 312 of the valve plate 300.

Accordingly, all of the refrigerant supplied to the input port 101 of the valve body 100 is cut off so that the refrigerant is not discharged to either of the first output port 102a and the second output port 102b.

In particular, the first through hole 311 and the second through hole 312 of the valve plate 300 are more reliably closed by the airtight member 400 provided in the rotary valve 200.

However, when the rotary valve 200 is further rotated counterclockwise by approximately 60 degrees by the step motor 520 of the driving member 500, as shown in FIG. 19, the rotary valve 200 is rotated. Only the expansion recess 210 of the valve 200 overlaps the first through hole 311 of the valve plate 300 while forming a fine expansion gap in the radial outer side.

At this time, the second through hole 312 of the valve plate 300 is maintained in a closed state by the rotary valve 200.

In particular, the second through hole 312 of the valve plate 300 is reliably closed by the airtight member 400 provided in the rotary valve 200, and the first through hole 311 is The expansion gap is formed between the expansion recess 210 which is the outer circumferential surface of the valve body 230 formed inside the expansion recess 210.

Accordingly, the refrigerant supplied to the input port 101 of the valve body 100 is an expansion gap formed between the expansion recess 210 of the rotary valve 200 and the first through hole 311 of the valve plate 300 After being expanded in, the air conditioner is cooled by being discharged to the first output port 102a.

Thereafter, when the rotary valve 200 is further rotated by about 60 degrees by the step motor 520 of the driving member 500 and the rotary valve 200 is positioned as shown in FIG. 20, the rotary valve 200 Since the passage hole 220 of the valve plate 300 overlaps with the first through hole 311 of the valve plate 300 in a wide cross-sectional area, expansion of the refrigerant does not occur and is in a completely open state.

At this time, the second through hole 312 of the valve plate 300 is continuously maintained in a closed state by the rotary valve 200.

In particular, the second through hole 312 of the valve plate 300 is more reliably closed by the airtight member 400 provided in the rotary valve 200.

Accordingly, the refrigerant supplied to the input port 101 of the valve body 100 passes through the flow path hole 220 of the rotary valve 200 and the first through hole 311 of the valve plate 300 as it is without expansion. After that, it is discharged to the first output port (102a).

And, when the rotary valve 200 is further rotated by approximately 60 degrees by the step motor 520 of the driving member 500 and the rotary valve 200 is positioned as shown in FIG. 21, the rotary valve 200 Both the expansion recess 210 and the flow path hole 220 of the valve plate 300 are again in a closed state that does not overlap with either the first through hole 311 and the second through hole 312.

Accordingly, all of the refrigerant supplied to the input port 101 of the valve body 100 is cut off again, so that the refrigerant is not discharged to either of the first output port 102a and the second output port 102b.

However, when the rotary valve 200 is further rotated counterclockwise by approximately 60 degrees by the step motor 520 of the driving member 500, as shown in FIG. 22, the rotary valve 200 is rotated. Only the expansion recess 210 of the valve 200 overlaps the second through hole 312 of the valve plate 300 while forming a fine expansion gap in the radial direction.

At this time, the first through hole 311 of the valve plate 300 is kept in a closed state by the rotary valve 200.

In particular, the first through hole 311 of the valve plate 300 is reliably closed by the airtight member 400 provided in the rotary valve 200, and the second through hole 312 is The expansion gap is formed between the expansion recess 210 which is the outer circumferential surface of the valve body 230 formed inside the expansion recess 210.

Accordingly, the refrigerant supplied to the input port 101 of the valve body 100 is an expansion gap formed between the expansion recess 210 of the rotary valve 200 and the second through hole 312 of the valve plate 300 After being expanded in, the air conditioner is heated by being discharged to the second output port 102b.

Thereafter, when the rotary valve 200 is further rotated by approximately 60 degrees by the step motor 520 of the driving member 500 and the rotary valve 200 is positioned as shown in FIG. 23, the rotary valve 200 Since the flow path hole 220 of the valve plate 300 overlaps with the second through hole 312 of the valve plate 300 in a wide cross-sectional area, expansion of the refrigerant does not occur and is in a completely open state.

At this time, the first through hole 311 of the valve plate 300 is continuously maintained in a closed state by the rotary valve 200.

In particular, the first through hole 311 of the valve plate 300 is more reliably closed by the airtight member 400 provided in the rotary valve 200.

Accordingly, the refrigerant supplied to the input port 101 of the valve body 100 passes through the flow path hole 220 of the rotary valve 200 and the second through hole 312 of the valve plate 300 without expansion. Then, it is discharged to the second output port (102b).

Therefore, the electronic expansion and direction change integrated valve of the present invention configured as described above enables precise control while simplifying the configuration of the vehicle air conditioner, and in particular, increases the airtightness of the refrigerant and the processability and productivity of the product, thereby increasing the production cost of the product. It is an invention with an excellent advantage of maximizing market competitiveness while lowering the value.

In particular, by forming two output ports (102a) (102b) in the valve body (100) and forming two through holes (311, 312) in the valve plate 300, one during cooling and heating of the heat pump. It is also possible to circulate the refrigerant through different paths through the expansion valve of.

The above embodiments are examples for specifically explaining the technical idea of the present invention, and the scope of the present invention is not limited to the above drawings or embodiments.

Claims

A valve body having an input port through which a refrigerant is supplied to one side, an output port through which the refrigerant is discharged to the other side, and a flow path communicating the input port and the output port therein;

Made in a plate shape, provided to be rotatable in a circumferential direction in the flow path between the input port and the output port, an expansion recess extending in a circumferential direction with a predetermined radial width, and an end of the expansion recess A rotary valve in communication with a flow path hole having a radial width greater than that of the expansion recess;

A valve plate formed in a plate shape, stacked and arranged to contact the rotary valve, fixed non-rotatably in the flow path of the valve body, and having a through hole formed in a circumferential direction;

An airtight member made of synthetic resin or an elastic airtight material and provided so as to be integrally rotatable on at least one surface of the rotary valve toward the valve plate to secure airtightness between the through hole of the valve plate and the rotary valve;

Electronic expansion and direction change integrated valve comprising a driving member for transmitting a rotational force to the rotary valve.
The electronic expansion and direction change integrated valve according to claim 1, wherein the expansion recesses overlap along the circumferential direction from the outer side in the radial direction of the through hole to form an expansion gap.
The method of claim 2, wherein the output ports of the valve body include a first output port and a second output port independently formed from each other;

The through-holes of the valve plate include first through-holes and second through-holes spaced apart from each other in a circumferential direction corresponding to the first output port and the second output port, respectively;

Electronic expansion and direction change integrated valve, characterized in that the refrigerant can be supplied by switching from one input port to one of two output ports.
The method of claim 3, wherein the airtight member and the rotary valve are formed in a polygonal shape or an arc shape that engages and engages with each other in contact with each other, so that the airtight member rotates integrally when the rotary valve is rotated. Electronic expansion and direction change integrated valve.
The method of claim 4, wherein the driving member comprises a shaft connected to a rotation center of the rotation valve and integrally rotating, and a step motor capable of controlling a rotation angle according to power control and transmitting rotational force to the shaft;

The valve plate is an integrated electronic expansion and direction change valve, characterized in that the support groove for rotatably supporting the lower end of the shaft is formed in the center.