KR101617825B1 - Control valve for an air-conditioner and an air-conditioner comprising the same for a vehicle - Google Patents

Control valve for an air-conditioner and an air-conditioner comprising the same for a vehicle Download PDF

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Publication number
KR101617825B1
KR101617825B1 KR1020100004919A KR20100004919A KR101617825B1 KR 101617825 B1 KR101617825 B1 KR 101617825B1 KR 1020100004919 A KR1020100004919 A KR 1020100004919A KR 20100004919 A KR20100004919 A KR 20100004919A KR 101617825 B1 KR101617825 B1 KR 101617825B1
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South Korea
Prior art keywords
refrigerant
port
needle
discharge
compressor
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KR1020100004919A
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Korean (ko)
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KR20110085244A (en
Inventor
이건호
장영일
Original Assignee
학교법인 두원학원
주식회사 두원전자
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Priority to KR1020100004919A priority Critical patent/KR101617825B1/en
Priority to PCT/KR2010/009549 priority patent/WO2011090276A2/en
Publication of KR20110085244A publication Critical patent/KR20110085244A/en
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Publication of KR101617825B1 publication Critical patent/KR101617825B1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3286—Constructional features
    • B60H2001/3297—Expansion means other than expansion valve

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

A variable displacement swash plate compressor which pressurizes a refrigerant sucked into the suction chamber from the evaporator and discharges the compressed refrigerant into a discharge chamber by using a plurality of reciprocating pistons coupled to a swash plate disposed in the crank chamber; A condenser for condensing the refrigerant introduced from the discharge chamber; and a controller for controlling the flow rate of the control refrigerant, which is installed in the compressor and is discharged from the discharge chamber through the high-pressure port and discharged to the crank chamber through the intermediate pressure port, And a control valve for controlling the operation capacity of the compressor by varying the inclination angle of the swash plate and discharging the refrigerant from the condenser through the inlet port to the evaporator through the discharge port, Thereby providing a harmonizing device.
Therefore, since the control valve can simultaneously perform the capacity control of the variable capacity compressor and the throttling control of the condensed refrigerant, a separate expansion valve for switching the condensed refrigerant is not necessary.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control valve for an air conditioner and an air conditioner for an automobile,

The present invention relates to a control valve for an air conditioner and an air conditioner for a vehicle. More particularly, the present invention relates to a control valve for an air conditioner capable of simultaneously controlling the capacity of a variable capacity compressor as well as throttling control of a condensed refrigerant, To an air conditioner for a vehicle.

Background Art [0002] In general, an air conditioner for a vehicle includes a compressor, a condenser, an expansion valve, and an evaporator. Various compressors may be used as the compressor, and a swash plate type compressor is widely used as a compressor of an air conditioner for an automobile. The swash plate type compressor is divided into various types according to the compression type and structure. Recently, a variable displacement swash plate type compressor capable of varying the compression capacity has been widely used.

In the variable displacement swash plate type compressor, the inclination of the swash plate is adjusted to adjust the capacity of the variable displacement compressor. That is, when the refrigerant inflow amount from the discharge chamber to the crank chamber of the variable displacement swash plate type compressor is increased, the pressure of the crank chamber is increased to reduce the inclination of the swash plate, and the capacity of the variable displacement swash plate type compressor is reduced . In order to adjust the inclination of the swash plate, a control valve is integrally installed in the variable displacement swash plate type compressor.

In the air conditioner, since the expansion valve is installed in addition to the control valve, not only the manufacturing cost is increased but also the size of the installation space is increased and the control logic for driving each of the two valves is synchronized There is a problem.

An object of the present invention is to provide a control valve for an air conditioner and an air conditioner for a vehicle that can simultaneously control the capacity of a variable capacity compressor as well as the throttling control of a condensed refrigerant.

A variable displacement swash plate compressor which pressurizes a refrigerant sucked into the suction chamber from the evaporator and discharges the compressed refrigerant into a discharge chamber by using a plurality of reciprocating pistons coupled to a swash plate disposed in the crank chamber; A condenser for condensing the refrigerant introduced from the discharge chamber; and a controller for controlling the flow rate of the control refrigerant, which is installed in the compressor and is discharged from the discharge chamber through the high-pressure port and discharged to the crank chamber through the intermediate pressure port, And a control valve for controlling the operation capacity of the compressor by varying the inclination angle of the swash plate and discharging the refrigerant from the condenser through the inlet port to the evaporator through the discharge port, Thereby providing a harmonizing device.

According to another aspect of the present invention, there is provided a refrigerator comprising: an evaporator for supplying cool air to a room of a vehicle; a plurality of pistons coupled to a swash plate disposed in the crank chamber to reciprocate, And a condenser for condensing the refrigerant flowing in from the discharge chamber, wherein the control valve is integrally provided in the compressor, and the control valve is provided integrally with the compressor, The control valve controls the operation amount of the compressor by varying the inclination angle of the swash plate by controlling the flow rate of the control refrigerant sucked through the high pressure port and discharged to the crank chamber through the intermediate pressure port to adjust the pressure of the crank chamber, The refrigerant flowing from the condenser is throttled through the discharge port, It provides for the air conditioner control valve to discharge groups.

The control valve for an air conditioner and the air conditioner for a vehicle according to the present invention have the following effects.

First, the control valve can simultaneously perform the throttling control of the condensed refrigerant as well as the capacity control of the variable displacement compressor. Therefore, a separate expansion valve for the expansion of the condensed refrigerant is unnecessary.

Second, since the expansion valve is unnecessary, not only the manufacturing cost is reduced but also the size of the installation space is reduced.

Third, since the above two functions can be performed by one control logic, the control logic is simplified.

1 is a schematic block diagram of an air conditioner for a vehicle according to an embodiment of the present invention.
Fig. 2 is a configuration diagram showing the operation of the control valve shown in Fig. 1. Fig.
3 is a partial sectional view showing the internal structure of the control valve shown in Fig.
4 is a graph showing the relationship between the flow rate of the control refrigerant and the throttling flow rate according to the operation capacity in the compressor shown in FIG.
FIG. 5 is a schematic view showing an open state of the control refrigerant passage and the throttle channel shown in FIG. 3 when the minimum capacity operation of the compressor provided with the control valve shown in FIG. 1 is performed.
FIG. 6 is a schematic view showing an open state of the control refrigerant passage and the throttle passage shown in FIG. 3 when the maximum capacity of the compressor provided with the control valve shown in FIG. 1 is operated.
7 is a cross-sectional view showing an internal structure of a control valve according to another embodiment of the present invention.
8 is a cross-sectional view illustrating an internal structure of a control valve according to another embodiment of the present invention.
Fig. 9 is a schematic diagram showing the operation principle of the control valve shown in Fig. 8. Fig.

Fig. 1 shows a schematic configuration diagram of a vehicle air conditioner 10 according to an embodiment of the present invention. 1, the air conditioner 10 includes a variable capacity swash plate type compressor 11, a condenser 12, an evaporator 13, and a control valve 100 do. The high-temperature, high-pressure refrigerant discharged from the compressor (11) is condensed in the condenser (12) and then throttled in the control valve (100). The throttled refrigerant is evaporated in the evaporator (13), and then sucked back into the compressor (11). The construction of the condenser 12 and the evaporator 13 can be variously selected by those skilled in the art, and a detailed description of the structure is omitted.

The compressor 11 is connected to a swash plate (not shown) disposed in a crank chamber (not shown) and uses a plurality of reciprocating pistons (not shown) And then discharged to a discharging chamber (not shown). The structure of the compressor 11 can be variously selected, for example, in Patent No. 529716, No. 515285, No. 572123, and the like.

The control valve 100 controls the refrigerant flowing from the condenser 12 to the evaporator 13 in a throttled manner and flows into the crank chamber of the compressor 11 from the discharge chamber of the compressor 11, (Not shown) is controlled. Fig. 2 is a structural view showing the operation of the control valve 100, and Fig. 3 is a schematic partial cross-sectional view showing the schematic internal structure of the control valve 100. As shown in Fig. Although the control valve 100 is integrally formed with the compressor 11 in the present embodiment, the present invention is not limited to this, and the control valve 100 may be integrally formed with the evaporator 13 have.

1 to 3, the control valve 100 includes a body 110, a valve unit 120, and a driving unit 130. The body 110 is formed in the through hole 115 along the vertical direction. The discharge port 111 is formed on the upper part of the body 110 and the inflow port 112 is formed on the upper side. The intermediate pressure port 114 is formed at a lower portion of the body 110, and the high pressure port 113 is formed at a lower side surface thereof. The discharge port 111 communicates with the inlet of the evaporator 13 and the inlet port 112 communicates with the outlet of the condenser 12. The intermediate pressure port 114 is in communication with the crank chamber of the compressor 11 and the high pressure port 113 is in communication with the discharge chamber of the compressor 11. The body 110 has a throttling flow path 116 for communicating the inflow port 112 with the discharge port 111. The control valve 114 is connected to the high pressure port 113 and the intermediate pressure port 114, A refrigerant passage 114 is formed. However, the present invention is not limited to the structure of the above-described body, and the ports 111, 112, 113 and 114 may be formed at various positions.

The valve portion 120 includes a needle 121, a first sleeve 122, and a second sleeve 123. The needle 121 is inserted into the through hole 115 and linearly moves in the vertical direction. The first sleeve 122 is inserted into the lower portion of the needle 111 and moves up and down together with the needle 111. The second sleeve 123 is inserted into the upper portion of the needle 111 and moves up and down together with the needle 111.

The first sleeve 122 controls the opening of the control refrigerant passage 117 in accordance with the upward and downward linear motion of the needle 121. The first sleeve 122 is formed to have a smaller radius toward the downward direction. Accordingly, as the needle 121 moves downward, the control refrigerant flow path 117 becomes narrower.

The first sleeve 122 controls the opening of the control refrigerant passage 117 in accordance with the upward and downward linear motion of the needle 121. The first sleeve 122 is formed to have a smaller radius toward the upper side. Accordingly, as the needle 121 moves upward, the throttling channel 116 becomes narrower.

The driving unit 130 may include a solenoid 130. The driving unit 130 may include a solenoid 130, The solenoid 130 applies an operating force to the needle 121 to linearly move the needle 121 in the vertical direction. The solenoid 130 includes a core 134, a coil 135, a plunger 136, a first spring 131, and a second spring 132. The core 134 is fixed within the body 110 and surrounds the needle 121. The core 134 guides the needle 121 to linearly move in the up-and-down direction. The coil 135 is fixed to the body 110 so as to surround the core 134. The plunger 136 is fixed to the center portion of the needle 121 and moves up and down together with the needle 121.

The first spring 131 is fixed between the plunger 136 and the inner surface of the center portion of the body 110 to apply a first elastic force to push the plunger 136 downward. The second spring 132 is disposed between the core 134 and the plunger 136 to apply a second elastic force to push the plunger 136 upward. When the compressor (11) is stopped, the plunger (136) is positioned at a position where the external force applied to the plunger (136) is balanced. In this embodiment, since the second elastic force is designed to be larger than the first elastic force, the plunger 136 is located at the uppermost position.

The operation of the control valve 100 will be described in detail with reference to FIGS. 2 and 4. FIG. 4 is a graph (f2) of the throttle refrigerant flow rate according to the graph (f1) of the control refrigerant flow rate according to the operating capacity of the compressor (11) and the operating capacity of the compressor (11). The compressor (11) is operated from the minimum capacity operation to the maximum capacity operation range. The control refrigerant flow rate gradually decreases as the operation capacity increases, and has a value of zero (0) at the maximum capacity operation. In FIG. 4, the control refrigerant flow rate is shown as a curve, but the present invention is not limited thereto.

Also, the throttle refrigerant flow rate gradually increases as the operating capacity of the compressor 11 increases. In the minimum capacity operation, the throttle refrigerant flow rate has a very low value, and the flow rate of the throttle refrigerant becomes maximum at the maximum capacity operation. In FIG. 4, the flow rate of the throttle refrigerant is shown as a curve, but the present invention is not limited thereto.

5 is a schematic view showing the open state of the control refrigerant passage 117 and the throttling oil passage 116 when the compressor 11 is operated at the minimum capacity. As described above, since the second elastic force is larger than the first elastic force, the downward movement of the needle 121 is restricted, and the control refrigerant passage 117 is kept at the maximum open state. Therefore, since the high-pressure refrigerant flows into the crank chamber of the compressor 11 from the discharge chamber of the compressor 11 at the maximum, the pressure of the crank chamber of the compressor 11 increases, The inclination is reduced. From this, the compressor (11) performs the minimum capacity operation. However, the second sleeve 123 closes most of the throttling flow path 116. Therefore, the amount of the refrigerant flowing into the evaporator 13 from the condenser 12 becomes the minimum value, and the refrigerant is throttled through the throttling channel 116.

The needle 121 is kept stationary by a difference between the second elastic force and the first elastic force until the current value applied to the solenoid 130 reaches a specific current value.

When the current value applied to the solenoid 130 is equal to or greater than the specific current value, the plunger 136 overcomes the difference between the second elastic force and the first elastic force and moves downward. The needle 121 moves downward together with the plunger 136. From this, the opening degree of the control refrigerant passage 117 decreases and the opening degree of the throttle shaft passage 116 increases. From this, the inclination of the swash plate (not shown) increases, and the flow rate of the throttle refrigerant flowing from the condenser 12 to the evaporator 13 increases.

If the current value reaches the maximum current value, the control refrigerant passage 117 is completely closed, and the throttling flow passage 116 is completely opened. At this time, the compressor 11 performs the maximum capacity operation. 4 is a schematic view showing the open state of the control refrigerant passage 117 and the throttling oil passage 116 when the compressor 11 is operating at the maximum capacity.

7 is a cross-sectional view showing the internal structure of the control valve 200 according to another embodiment of the present invention. The same reference numerals as in the above-described embodiments denote the same members. Hereinafter, differences from the above-described embodiment will be mainly described.

The control valve 200 includes a body 210, a driving unit 230, a first valve unit 220, and a second valve unit 240. The body 210 defines a high pressure port 213, a medium pressure port 214, an inlet port 212, and a discharge port 211. The body 210 is formed in the through hole 215 along the vertical direction. The discharge port 211 communicates with the inlet of the evaporator 13 and the inlet port 212 communicates with the outlet of the condenser 12. The intermediate pressure port 214 is in communication with the crank chamber of the compressor 11 and the high pressure port 213 is in communication with the discharge chamber of the compressor 11. A bellows flow passage 216 is formed in the body 210 so as to communicate the inlet port 212 and the discharge port 211. A control for connecting the high pressure port 213 and the intermediate pressure port 214 A refrigerant flow path 217 is formed.

The first valve portion 220 includes a needle 221 and a sleeve 222. The sleeve 222 controls the opening of the control refrigerant passage 217 in accordance with the upward and downward linear motion of the needle 221.

The driving unit 230 includes a solenoid 230. The solenoid 230 applies an operating force to the needle 221 to linearly move the needle 221 in the vertical direction. The solenoid 230 includes a core 234, a coil 235, a plunger 236, a first spring 231, and a second spring 232. Since the second elastic force of the second spring 232 is larger than the first elastic force of the first spring 231, the needle 221 is moved downward until a current equal to or greater than a set value is applied to the coil 235 Is limited. However, the structure and operation of the driving unit 230 are similar to those of the above-described embodiment, and a detailed description thereof will be omitted.

The second valve portion 240 includes an orifice 241. The orifice (241) is provided on the throttling flow path (216). Accordingly, the throttling flow rate flowing into the evaporator 13 from the condenser 12 is controlled by the orifice 241, and the refrigerant is throttled while passing through the orifice 241. In the present embodiment, the orifice 241 is formed so as to protrude from the body 210. The present invention is not limited thereto, and the orifice 241 may be separately formed and then inserted and fixed to the body 210.

FIG. 8 is a cross-sectional view showing an internal structure of a control valve 300 according to another embodiment of the present invention, and FIG. 9 is a schematic structural view showing the operation principle of the control valve 300. The same reference numerals as in the above-described embodiments denote the same members. Hereinafter, differences from the above-described embodiment will be mainly described.

The control valve 300 includes a body 310, a first driving part 330, a second driving part 350, a first valve part 320 and a second valve part 340. The body 310 defines a high pressure port 313, a medium pressure port 314, an inlet port 312, and a discharge port 311. The body 310 is formed in the first through hole 315 along the vertical direction. The discharge port 311 communicates with the inlet of the evaporator 13 and the inlet port 312 communicates with the outlet of the condenser 12. The intermediate pressure port 314 is in communication with the crank chamber of the compressor 11 and the high pressure port 313 is in communication with the discharge chamber of the compressor 11. The body 310 is provided with a throttling flow path 316 for communicating the inflow port 312 and the discharge port 311 and is provided with a control for communicating the high pressure port 313 and the intermediate pressure port 314 A refrigerant passage 317 is formed.

The first valve portion 320 includes a first needle 321 and a first sleeve 322. The first sleeve 322 controls the opening of the control refrigerant passage 317 in accordance with the upward / downward linear movement of the first needle 321.

The first driving unit 330 includes a solenoid 330. The solenoid 330 applies an operating force to the first needle 321 to linearly move the first needle 321 in the first through hole 315 in the vertical direction. The solenoid 330 includes a core 334, a coil 335, a plunger 336, a first spring 331, and a second spring 332. The structure and operation of the first driver 330 are similar to those of the first embodiment, and detailed description thereof will be omitted.

The evaporator discharging refrigerant bypass port 318 through which the refrigerant discharged from the evaporator 13 flows and the refrigerant flowing into the bypass port 318 are discharged to the inlet of the compressor 11 The evaporator discharge refrigerant return port 319 is formed. The inflow port 312 and the discharge port 311 are perpendicular to each other and the bypass port 318 and the return port 319 are perpendicular to each other.

A throttling channel 316 is formed between the bypass port 318 and the return port 319. The second valve portion 340 includes a second needle 341 and a second sleeve 342. The second sleeve 342 is installed on the throttling channel 316 to regulate the opening of the throttling channel 316. A third spring 365 is inserted between the sleeve support member 360 and the plug 361 so that the second sleeve 342 is supported upward by the sleeve support member 360.

A second through hole 366 is formed in the body 310 along the vertical direction. The second needle 341 is inserted into the second through hole 366 and linearly moves in the vertical direction. The second sleeve 342 is fixed to the lower end of the needle 341.

The second driving unit 350 is driven using the principle of the diaphragm and includes a diaphragm 351 and an outer case 352. The outer case 352 is coupled to the upper portion of the body 310. The space between the diaphragm 351 and the outer case 352 is an upper pressure chamber 353. A temperature-sensitive gas is enclosed in the upper pressure chamber 353, and the upper pressure chamber 353 is sealed by a sealing member 354.

The lower pressure chamber 356 of the diaphragm 351 is provided with a stopper 355. The second needle 342 is fixed to the stopper 355 so that the movement of the diaphragm 351 linearly moves the second needle 342 in the vertical direction.

And the refrigerant flows from the outlet of the evaporator (13) through the bypass port (318). The introduced refrigerant changes the temperature of the temperature-sensitive gas in the upper pressure chamber 353 through the lower pressure chamber 356, and the diaphragm 351 is moved by the temperature change of the temperature-sensitive gas. By the movement of the diaphragm 351, the second sleeve 342 moves to adjust the opening of the throttle channel 316. Accordingly, the control valve 300 is actively and regulates the throttle refrigerant flow rate independently of the control refrigerant, based on the refrigerant temperature at the outlet of the evaporator 13.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the disclosed exemplary embodiments, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims. Accordingly, the true scope of the present invention should be determined by the technical idea of the appended claims.

10: vehicle air conditioner 11: variable capacity swash plate compressor
12: condenser 13: evaporator
100, 200, 300: control valve 110, 210, 310: body
111, 211, 311: inlet port 112, 212, 312: discharge port
113, 213, 313: High pressure port 114, 214, 314: Medium pressure port
115: through holes 116, 216, 316:
117, 217, 317: Control refrigerant channel 120:
121: Needle 122: First sleeve
123: second sleeve 130, 230, 330: solenoid
131, 231, 331: first spring 132, 232, 332: second spring
134, 234, 334: core 135, 235, 335: coil
136, 236, 336: plunger 318: bypass port
319: liter port

Claims (15)

evaporator;
A variable displacement swash plate compressor using a plurality of reciprocating pistons coupled to a swash plate disposed in the crank chamber to pressurize the refrigerant sucked into the suction chamber from the evaporator and discharge the refrigerant into the discharge chamber;
A condenser for condensing the refrigerant introduced from the discharge chamber; And
The operation amount of the compressor is controlled by changing the inclination angle of the swash plate by adjusting the flow rate of the control refrigerant sucked from the discharge chamber through the high pressure port and discharged to the crank chamber through the intermediate pressure port, And a control valve for throttling refrigerant flowing in from the condenser through an inlet port and discharging the refrigerant to the evaporator through a discharge port. The method according to claim 1,
Wherein the control valve comprises:
A body defining the high pressure port, the intermediate pressure port, the inlet port, and the discharge port;
A driving unit installed on the body and generating a driving force; And
And a valve unit that moves by the driving force of the driving unit and regulates the flow rate of the control refrigerant and adjusts the degree of the switching. The method of claim 2,
The valve unit includes:
A needle installed on the body and moved by the driving unit;
A first sleeve coupled to the needle and integrally moving with the needle, the first sleeve adjusting the opening of the control refrigerant passage communicating the high pressure port and the intermediate pressure port; And
And a second sleeve coupled to the needle to move integrally with the needle and to adjust an opening degree of a throttle passage communicating the inlet port and the discharge port. The method of claim 3,
Wherein the body is formed with a through hole along a vertical direction, the needle is inserted in the through hole so as to be movable in the up and down direction,
Wherein the driving unit includes a solenoid for applying an operating force to linearly move the needle in the up-and-down direction. The method of claim 4,
The solenoid includes:
A core fixed within the body and surrounding the needle, the guide guiding the needle linearly in the vertical direction;
A coil disposed to surround the core; And
And a plunger fixed to an intermediate portion of the needle and moving up and down linearly with the needle. The method of claim 5,
The solenoid includes:
A first spring disposed between the plunger and the inner surface of the body for applying a first elastic force to push the plunger downward; And
And a second spring disposed between the core and the plunger for applying a second elastic force to push the plunger upward. The method of claim 6,
The discharge port is formed in an upper portion of the body, an inflow port is formed in an upper side, a middle pressure port is formed in a lower portion, a high pressure port is formed in a lower side,
Wherein the first sleeve is fixed to a lower portion of the needle, and the second sleeve is fixed to an upper portion of the needle. The method of claim 7,
Wherein the needle moves downward by the driving force as the operating capacity of the compressor increases. The method of claim 3,
The first sleeve adjusts the opening degree of the control refrigerant passage to be the maximum, and the second sleeve adjusts the opening degree of the throttle passage to be minimum,
Wherein the first sleeve adjusts the opening of the control refrigerant passage to a minimum when the maximum capacity operation is performed, and the second sleeve adjusts the opening of the throttle passage to be the maximum. The method according to claim 1,
Wherein the control valve comprises:
A body defining the high pressure port, the intermediate pressure port, the inlet port, and the discharge port;
A driving unit installed on the body and generating a driving force;
A first valve unit that moves by the driving force of the driving unit and actively regulates a flow rate of the control refrigerant; And
And a second valve portion for passively performing the flow rate of the throttle refrigerant. The method of claim 10,
The second valve portion
And an orifice provided on a throttle channel communicating the inflow port and the discharge port. The method according to claim 1,
Wherein the control valve comprises:
A body defining the high pressure port, the intermediate pressure port, the inlet port, and the discharge port;
A first driver installed in the body and generating a driving force;
A first valve unit that moves by the driving force of the first driving unit and regulates a flow rate of the control refrigerant;
A second driving unit installed on the body and generating a driving force based on a discharge temperature of the evaporator; And
And a second valve portion that is moved by the driving force of the second driving portion and adjusts a flow rate of the throttle refrigerant. The method of claim 12,
The body further includes an evaporator discharge refrigerant return port through which the refrigerant discharged from the evaporator flows and an evaporator discharge refrigerant return port through which the refrigerant introduced into the evaporator discharge refrigerant bypass port flows back to the compressor,
Wherein the second driving unit controls the opening degree of the throttle channel communicating the inlet port and the discharge port by using the second valve unit based on the temperature of the refrigerant flowing from the evaporator discharging refrigerant bypass port, Device. The method according to any one of claims 1 to 13,
Wherein the control valve is installed integrally with any one of the evaporator and the compressor. A variable displacement swash plate which pressurizes the refrigerant sucked into the suction chamber from the evaporator and discharges the refrigerant into the discharge chamber by using a plurality of reciprocating pistons coupled to the swash plate disposed in the crank chamber, A control valve for an air conditioner, comprising: a compressor; and a condenser for condensing the refrigerant introduced from the discharge chamber,
And the control valve controls the flow rate of the control refrigerant discharged from the discharge chamber through the high pressure port to the crank chamber through the intermediate pressure port to adjust the pressure of the crank chamber so that the inclination angle of the swash plate To control the operation capacity of the compressor, to throttle the refrigerant flowing from the condenser through the inlet port, and to discharge the refrigerant to the evaporator through the discharge port.
KR1020100004919A 2010-01-19 2010-01-19 Control valve for an air-conditioner and an air-conditioner comprising the same for a vehicle KR101617825B1 (en)

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KR1020100004919A KR101617825B1 (en) 2010-01-19 2010-01-19 Control valve for an air-conditioner and an air-conditioner comprising the same for a vehicle
PCT/KR2010/009549 WO2011090276A2 (en) 2010-01-19 2010-12-30 Control valve for an air conditioner, and air conditioner for a vehicle

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KR101617825B1 true KR101617825B1 (en) 2016-05-04

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Citations (1)

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JP2002206822A (en) * 2001-01-10 2002-07-26 Fuji Koki Corp Freezing cycle device
JP2005098197A (en) * 2003-09-04 2005-04-14 Tgk Co Ltd Capacity control valve for variable displacement compressor
JP2005351207A (en) * 2004-06-11 2005-12-22 Tgk Co Ltd Control valve for variable displacement compressor
KR101451808B1 (en) * 2008-04-25 2014-10-16 한라비스테온공조 주식회사 Cooling system of air conditioner for vehicles

Patent Citations (1)

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Publication number Priority date Publication date Assignee Title
JP2008297974A (en) 2007-05-31 2008-12-11 Fuji Koki Corp Control valve for variable displacement compressor

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