WO2011078547A2

WO2011078547A2 - Variable capacity compressor

Info

Publication number: WO2011078547A2
Application number: PCT/KR2010/009147
Authority: WO
Inventors: 이건호; 김기범
Original assignee: 두원공과대학교; 주식회사 두원전자; 이태진
Priority date: 2009-12-23
Filing date: 2010-12-21
Publication date: 2011-06-30
Also published as: WO2011078547A3

Abstract

The present invention relates to a variable capacity compressor. The variable capacity compressor, comprises: an intake seal, a crank seal and a discharge seal; a discharge outlet connected to said discharge seal and mounted to a discharge passage; and a check valve which opens and closes the discharge passage based on the pressure differentials in the intake seal, crank seal and discharge seal. Accordingly, the differential, between the check valve inlet and outlet pressures and the discharge pressure at the exit, are minimized by allowing the pressures of intake and crank seals to act upon the far-side of the valve body such that the pressure in the direction opposite to the discharge seal, is reduced.

Description

Capacity variable compressor

The present invention relates to a variable displacement compressor, and more particularly, to a variable displacement compressor that minimizes the difference between the inlet side discharge pressure and the outlet side discharge pressure of the check valve.

Since the compressor included in the cooling system of the automotive air conditioner is directly connected to the engine through the belt, the rotation speed cannot be controlled.

Therefore, in recent years, a variable capacity compressor that can change the discharge amount of the refrigerant to obtain a cooling capacity without being regulated by the rotational speed of the engine has been used a lot.

Various types of variable displacement compressors are disclosed, such as swash plate type, rotary type and scroll type.

In the swash plate type compressor, the swash plate provided so that the inclination angle is variable in the crank chamber rotates according to the rotational motion of the rotating shaft, and the piston reciprocates by the rotational motion of the swash plate. In this case, the refrigerant in the suction chamber is sucked into the cylinder by the reciprocating motion of the piston, compressed and discharged into the discharge chamber. The inclination angle of the swash plate is changed according to the pressure difference in the crank chamber and the pressure in the suction chamber, and the discharge amount of the refrigerant is changed. Will be controlled.

In particular, it is common to adopt the solenoid type capacity control valve to adjust the pressure of the crankcase by opening and closing the valve by energization, and thereby adjusting the discharge capacity by adjusting the inclination angle of the swash plate.

At this time, the operation of the capacity control valve is calculated by a control unit in which a signal such as the detected engine speed, the temperature inside or outside the vehicle, the evaporator temperature, or the like is incorporated by the CPU, and based on the result of the calculation, the current By sending it to an electromagnetic coil.

In addition, a check valve is provided at the discharge port communicating with the discharge chamber to prevent the leakage of the refrigerant during the minimum capacity operation of the compressor.

Hereinafter, a structure of a check valve according to the related art will be described with reference to the drawings.

1 is a longitudinal sectional view showing a check valve of a variable displacement compressor according to the prior art.

As shown in FIG. 1, the check valve 1 according to the related art includes a valve housing 2 in which a refrigerant inlet 2a through which discharged refrigerant is introduced and a refrigerant outlet 2b through which discharged refrigerant is discharged are respectively formed. And a valve body 3 for reciprocating the inside of the valve housing 2 to open and close the refrigerant inlet 2a and the refrigerant outlet 2b, and a cover 4 covering the open end of the valve housing 2. And a spring 5 interposed between the cover 4 and the valve body 3.

The check valve 1 configured as described above is installed at the discharge port of the compressor to prevent leakage of the refrigerant during the minimum capacity operation (at low pressure discharge).

However, according to the check valve 1 of the prior art, the pressure difference between the input side discharge pressure PdH and the output side discharge pressure PdL is generated by the spring 5, which causes the compressor operating conditions to be inferior. There was a problem of this deterioration.

That is, the inlet discharge pressure PdH flowing into the first refrigerant inlet 2a pressurizes the upper portion of the valve body 3 and simultaneously compresses the spring 5 so that the pressure is lowered. The pressure PdL is sent to the next cooling cycle through the refrigerant outlet 2b.

As a result, the output discharge pressure PdL discharged to the refrigerant discharge port 2b is lower than the inlet discharge pressure PdH flowing into the first refrigerant inlet 2a.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned general problems, and an object of the present invention is to provide a check valve with an inlet discharge pressure of a check valve by actuating a crankcase or a suction chamber pressure that increases or decreases in a direction opposite to the discharge chamber pressure. It is to provide a variable displacement compressor that minimizes the difference between the discharge pressure of the outlet and the outlet.

Another object of the present invention is to provide a variable displacement compressor configured to close the check valve by the pressure of the reverse flow refrigerant discharged during the minimum inclination angle of the swash plate to prevent the reverse flow of the discharge refrigerant.

According to one aspect of the present invention, there is provided a variable displacement compressor including: a discharge flow passage connected to the discharge chamber, the displacement variable compressor having a suction chamber, a discharge chamber, and a crank chamber; And a check valve mounted in the discharge passage to open and close the discharge passage by a differential pressure between the discharge chamber pressure and the crank chamber or suction chamber pressure.

The check valve may further include a valve housing having a first refrigerant inlet through which the discharge chamber pressure acts and a refrigerant outlet connected to the first refrigerant inlet, and having an end portion opposite to the first refrigerant inlet; A valve body for opening and closing the first refrigerant inlet; A cover having a second refrigerant inlet through which the crank chamber or suction chamber pressure is applied and covering the open end of the valve housing; And a biasing member interposed between the cover and the valve body.

Preferably, the valve body is composed of a large diameter portion corresponding to the first refrigerant inlet and a small diameter portion corresponding to the second refrigerant inlet.

On the other hand, it is preferable that an elastic member is interposed between the large diameter portion and the small diameter portion.

In addition, the large diameter portion is preferably formed with a seating groove in which the elastic member is seated.

The check valve preferably opens the discharge passage when the discharge chamber pressure is larger than the elastic force of the biasing member plus the pressure of the crank chamber or the suction chamber.

On the other hand, the valve body is preferably composed of a first valve body for opening and closing the first refrigerant inlet and a second valve body corresponding to the second refrigerant inlet.

In addition, it is preferable that the first valve body is formed with a hydraulic pressure portion to which the discharged backflow refrigerant acts, and the second valve body has a support portion inserted into the hydraulic pressure portion.

In addition, the hydraulic portion is preferably formed with a guide portion is inserted into the support portion to hold the initial position.

On the other hand, the guide portion is preferably an inclined portion that narrows in the insertion direction.

In addition, it is preferable that the biasing member is seated on the radially outer side of the guide part.

In addition, the crank chamber or the suction chamber is preferably provided with a connection passage for connecting the check valve.

According to the variable displacement compressor according to the present invention, the difference between the inlet side discharge pressure and the outlet side discharge pressure of the check valve is minimized by acting on the small diameter portion of the valve body to increase or decrease the crankcase or suction chamber pressure in a direction opposite to the discharge chamber pressure. It is effective.

In addition, when the reverse flow refrigerant discharged from the hydraulic portion of the first valve body acts during the minimum inclination angle driving of the swash plate, the first valve body has an effect of preventing the reverse flow of the discharge refrigerant by closing the first refrigerant inlet.

Accordingly, the reverse flow of the discharge refrigerant is blocked to prevent the durability of the swash plate due to the rapid flow sound and the crankcase pressure increase due to the refrigerant flow.

2 is a longitudinal sectional view showing the structure of a variable displacement compressor according to the present invention.

3 is a side cross-sectional view illustrating a rear housing of the variable displacement compressor of FIG. 2.

4 is a longitudinal sectional view showing a structure of a check valve according to a first embodiment of the present invention.

5 is a longitudinal sectional view showing a structure of a check valve according to a second embodiment of the present invention.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings.

First, the structure of the variable displacement swash plate compressor provided with a valve assembly according to the present invention will be described schematically.

Figure 2 is a longitudinal sectional view showing a structure of a variable displacement compressor according to the present invention, Figure 3 is a side cross-sectional view showing a rear housing of the variable displacement compressor of Figure 2, Figure 4 is a check according to a first embodiment of the present invention 5 is a longitudinal sectional view showing the structure of a valve, and FIG. 5 is a longitudinal sectional view showing the structure of a check valve according to a second embodiment of the present invention.

As shown, the variable displacement swash plate type compressor C has a cylinder block 10 having a plurality of cylinder bores 12 formed parallel to the inner circumferential surface in the longitudinal direction, and sealed in front of the cylinder block 10. The front housing 16 is coupled, and the rear housing 18 is hermetically coupled via a valve plate 20 at the rear of the cylinder block 10.

The crank chamber 86 is provided inside the front housing 16, and one end of the drive shaft 44 is rotatably supported near the center of the front housing 16, while the other end of the drive shaft 44 is Passed through the crank chamber 86 is supported via a bearing provided in the cylinder block 10.

In the crank chamber 86, the lug plate 54 and the swash plate 50 are provided around the drive shaft 44.

In the lug plate 54, a pair of power transmission support arms 62 each having a linearly perforated guide hole 64 formed at the center thereof are formed to protrude integrally on one surface, and one surface of the swash plate 50 has a ball. As the lug plate 54 rotates, the ball 66 of the swash plate 50 slides in the guide hole 64 of the lug plate 54 so that the swash plate 50 can be rotated. The inclination angle is variable.

In addition, the outer circumferential surface of the swash plate 50 is fitted to the piston 14 so as to be able to slide through the shoe 76.

Accordingly, as the swash plate 50 rotates in an inclined state, the pistons 14 fitted through the shoe 76 on the outer circumferential surface thereof are reciprocated in each cylinder bore 12 of the cylinder block 10. do.

In addition, a suction chamber 22 and a discharge chamber 24 are formed in the rear housing 18, and each cylinder bore is provided in the valve plate 20 interposed between the rear housing 18 and the cylinder block 10. The intake valve 32 and the discharge valve 36 are formed in the place corresponding to (12), respectively.

By the reciprocating motion of the piston 14, the refrigerant in the suction chamber 22 is sucked into the cylinder bore 12, compressed, and discharged to the discharge chamber 24. The pressure in the crank chamber 86 and the suction chamber ( 22) or the inclination angle of the swash plate 50 is changed in accordance with the pressure difference in the discharge chamber 24 to adjust the discharge amount of the refrigerant, which adjusts the pressure of the crank chamber 86 by opening and closing the valve by energization. It is usually implemented by the capacity control valve 200 to adjust the inclination angle of the swash plate 50 to adjust the discharge capacity.

In addition, a discharge flow path 101 communicating with the discharge chamber 24 is formed in the rear housing 18. At this time, the discharge passage 101 is provided with a check valve 100 for discharging the refrigerant compressed at a predetermined differential pressure or more to an external cooling cycle (condenser) and at the same time to prevent the reverse flow of the discharged refrigerant.

In addition, the discharge port 25 is preferably formed on the discharge side of the discharge passage 101.

In addition, the rear housing 18 is formed with a connection passage 102 for connecting the pressures Pc and PS of the crank chamber 86 or the suction chamber 22 to act on the check valve 100.

The compressor described above is just one example in which the check valve according to the present invention is installed, and is applicable to all other clutch-less displacement variable compressors.

Hereinafter, a check valve 100 according to the present invention will be described with reference to the drawings.

제1실시예First embodiment

2 to 4, the check valve 100 according to the first embodiment of the present invention is mounted in the discharge passage 101, the discharge chamber 24 pressure (Pd) and the crank chamber 86 Alternatively, the check valve 100 according to the present invention, which opens and closes the discharge flow path 101 by the differential pressures of the pressures Pc and Ps of the suction chamber 22, performs the next cooling cycle on the refrigerant discharged from the discharge chamber 24. By repeatedly performing the action of sending to the condenser, the valve housing 110, the valve body 120 for reciprocating the inside of the valve housing 110, and the open of the valve housing 120 A cover 130 covering an end portion and a biasing member 140 interposed between the cover 130 and the valve body 120 are included.

First, the valve housing 110 is connected to the first refrigerant inlet 111 according to the reciprocating movement of the first refrigerant inlet 111 and the valve body 120 in which the discharge chamber 24 pressure Pd is applied. The refrigerant outlet 112 is formed.

In this case, the first refrigerant inlet 111 is connected to the discharge chamber 24 by the discharge passage 101, and the first refrigerant outlet 112 is connected to the discharge outlet 25 by the discharge passage 101. . That is, the valve housing 110 is installed in the discharge passage 101.

In addition, the valve body 120 opens and closes the aforementioned first refrigerant inlet 111 by the pressure Pd of the discharge chamber 24.

In addition, the cover 130 is formed with a second refrigerant inlet 131 in which the crank chamber 86 or the suction chamber 22 pressures Pc and Ps act. In other words. The second refrigerant inlet 131 is connected to the connection passage 102.

On the other hand, the biasing member 140 is formed of a spring to apply an elastic force in the direction in which the valve body 120 closes the first refrigerant inlet 111.

The biasing member 140 may adjust the pressure difference of opening and closing the valve body 120 according to the size of the elastic modulus.

In addition, the valve body 120 corresponds to the first refrigerant inlet 111 and corresponds to the large diameter portion 121 and the second refrigerant inlet 131 on which the discharge chamber 24 pressure Pd acts, and the crank chamber. 86 or a small diameter portion 122 in which the suction chamber 22 pressures Pc and Ps act.

According to the check valve 100 of the present invention configured as described above, the size of the discharge chamber 24 pressure Pd is equal to the elastic force of the biasing member 140 and the pressure Pc of the crank chamber 86 or the suction chamber 22. When larger than Ps), the discharge passage 101 is opened.

For example, when the elastic force of the biasing member 140 is 50 and the pressures Pc and Ps of the crank chamber 86 or the suction chamber 22 are 50, the discharge chamber 24 pressure Pd is 100 or more. The check valve 100 is to open the discharge flow path 101.

At this time, since the pressures Pc and Ps of the crank chamber 86 or the suction chamber 22 increase and decrease in the opposite direction to the discharge chamber pressure Pd, the inlet side discharge pressure PdH and the outlet of the check valve 100 are The difference in the side discharge pressure PdH is minimized.

That is, when the pressure Pd of the discharge chamber 24 is increased, the pressures Pc and Ps of the crank chamber 86 or the suction chamber 22 are lowered, which causes the small diameter portion 122 of the valve body 120 to be lowered. As the pressure acting on the lower end of the valve body 120 opening the first refrigerant inlet 111 will be easier. As a result, as the force applied to the large diameter portion 121 of the valve body 120 decreases, the pressure loss of the refrigerant in the discharge chamber 22 moving inside the check valve 100 is minimized.

On the other hand, the pressure Pc and Ps of the crank chamber 86 or the suction chamber 22 is equal to the sum of the elastic force of the biasing member 140 and the pressures Pc and Ps of the crank chamber 86 or the suction chamber 22. As the specific gravity increases, the difference between the inlet-side discharge pressure PdH and the outlet-side discharge pressure PdL of the check valve 100 may be further reduced.

This is because the elastic force of the biasing member 140 is a fixed value and the pressures Pc and Ps of the crank chamber 86 or the suction chamber 22 vary in the opposite direction to the pressure Pd of the discharge chamber 24. This is because the range that can reduce the reaction force in the direction in which the valve body 120 is opened increases.

For example, when the elastic force of the biasing member 140 is 10 and the pressures Pc and Ps of the crank chamber 86 or the suction chamber 22 are 90, the discharge chamber 24 pressure Pd is actually the biasing member ( If only the force of the elastic force of 10 or more of the 140 is consumed, the check valve 100 is opened. That is, the pressures Pc and Ps of the crank chamber 86 or the suction chamber 22 increase or decrease in a direction opposite to the pressure Pd of the discharge chamber 24, so that the pressure of the crank chamber 86 or the suction chamber 22 is increased. (Pc, Ps) 90 is canceled by the pressure Pd of the discharge chamber 24.

In addition, the crank chamber 86 or the suction chamber pressure Pc acts on the small diameter portion 122 of the valve body 120 even when the elastic force decreases as the compression and swelling of the biasing member 140 are repeated. You can also completely block backflow.

On the other hand, (a) of FIG. 4 shows that the valve body 120 compresses the biasing member 140 by the discharge chamber 24 pressure Pd, and then cools the compressed refrigerant by opening the first refrigerant inlet 111. 4 (b) is driven at the minimum inclination angle of the swash plate 50 so that the elastic force and the crank chamber 86 pressure Pc of the biasing member 140 are applied to the valve body 120. The valve body 120 acts to close the first refrigerant inlet 111 to prevent backflow of the refrigerant.

In addition, the large diameter portion 121 and the small diameter portion 122 is interposed between the elastic member 150, the large diameter portion 121 is formed with a seating groove 151 for mounting the elastic member 150.

제2실시예Second embodiment

As shown in Figs. 2 to 3 and 5, the discharge passage 101 is mounted in the discharge passageway 101, and the pressure Pd of the discharge chamber 24 and the crank chamber 86 or the suction chamber 22 pressures Pc and Ps. The check valve 100 according to the present invention, which opens and closes the discharge passage 101 by differential pressure, repeatedly performs a function of sending the refrigerant discharged from the discharge chamber 24 to the next cooling cycle (condenser). And the valve housing 110, the valve body 120 for reciprocating the inside of the valve housing 110, the cover 130 and the cover 130 covering the open end of the valve housing 120 and And a biasing member 140 interposed between the valve bodies 120.

First, the valve housing 110 has a refrigerant connected to the refrigerant inlet 111 according to the reciprocating movement of the first refrigerant inlet 111 and the valve body 120 in which the discharge chamber 24 pressure Pd is applied. An outlet 112 is formed.

In this case, the first refrigerant inlet 111 is connected to the discharge chamber 24 by the discharge passage 101, and the refrigerant outlet 112 is connected to the discharge outlet 25 by the discharge passage 101. That is, the valve housing 110 is installed in the discharge passage 101.

In addition, the valve body 120 opens and closes the aforementioned first refrigerant inlet 111 by the pressure Pd of the discharge chamber 24. In addition, the valve body 120 has a reverse flow refrigerant discharged during the driving of the minimum inclination angle of the compressor, which will be described later.

In addition, the cover 130 is formed with a second refrigerant inlet 131 in which the crank chamber 86 or the suction chamber pressures Pc and Ps act. That is, the second refrigerant inlet 131 is connected to the connection passage 102.

In addition, the valve body 120 includes a first valve body 121 that opens and closes the first refrigerant inlet 111, and a second valve body 122 corresponding to the second refrigerant inlet 112. The first and

second valve bodies

121 and 122 are separately configured to move, respectively.

On the other hand, the biasing member 140 preferably applies an elastic force to the first valve body 121.

In addition, the first valve body 121 is formed with a pressure receiving portion 121a to which discharged backflow refrigerant acts, and the second valve body 122 has a support portion 122a inserted into the hydraulic pressure portion 121a. A) is formed.

In addition, the hydraulic pressure portion 121a is formed with a guide portion 150 into which the support portion 122a is inserted to hold an initial position, and the guide portion 150 is preferably an inclined portion that narrows in the insertion direction.

In addition, the biasing member 140 is seated on the radially outer side of the guide part 150.

That is, the check valve 100 of the present invention prevents the reverse flow of the discharged refrigerant even when the differential pressure is increased as shown in Table 1 below when the reverse flow refrigerant discharged to the hydraulic unit 121a operates. Done.

Table 1

According to the check valve 100 of the present invention configured as described above, the first valve body 121 by the reverse flow refrigerant discharged to the hydraulic pressure portion 121a of the first valve body 121 when the swash plate 50 is driven at the minimum inclination angle. ) Closes the first refrigerant inlet 111 to prevent backflow of the discharged refrigerant.

At this time, the elastic force of the biasing member 140 also acts on the first valve body 121.

Accordingly, the reverse flow of the discharged refrigerant is blocked to prevent the durability of the swash plate 50 due to the rapid flow sound and the increase in the pressure of the crank chamber 86 due to the refrigerant flow.

That is, the differential pressure is higher than the above-described [Table 1] and the set pressure by the action of the reverse flow refrigerant discharged to the second valve body 122 and the first valve body 121 and the hydraulic pressure unit 121a reciprocating respectively. In this case, the reverse flow of the discharged refrigerant is completely blocked.

Subsequently, when the set differential pressure is lowered, the crank chamber 86 or the suction chamber 22 pressures Pc and Ps are transmitted to the second refrigerant inlet 131 to act on the lower portion of the second valve body 122. The second valve body 122, which receives the pressure Pc and Ps of the suction chamber 22, rises, and the support part 122a supports the lower part of the hydraulic pressure part 121a so that the first refrigerant inlet 111 ) Will remain closed.

That is, the pressure Pc, Ps of the crank chamber 86 or the suction chamber 22 rises at the time of driving the minimum inclination angle of the swash plate 50, and the pressure Cc of the raised crank chamber 86 or the suction chamber 22 is increased. Ps) is to act on the check valve 100 through the connection flow path (102). At this time, in use of the compressor, the crankcase pressure Pc and the suction chamber pressure Ps become approximately equal.

Meanwhile, in FIG. 5A, the valve body 120 compresses the biasing member 140 by the pressure Pd of the discharge chamber 24 and then cools the compressed refrigerant by opening the first refrigerant inlet 111. The discharge (FULL OPEN) to the cycle (condenser), Figure 5 (b) is the reverse flow refrigerant discharged to the water pressure portion 121a of the first valve sleeve 121 when driven at the minimum inclination angle of the swash plate 50 It acts to raise only the first valve body 121 to close the first refrigerant inlet 111 (BACK FLOW CLOSE) to prevent the backflow of the refrigerant. In FIG. 5C, the crank chamber 86 or the suction chamber 22 pressures Pc and Ps act on the second valve body 122 so that the support part 122a of the second valve body 122 becomes the first. By supporting the pressure receiving portion 121a of the valve body 121 to close the first refrigerant inlet 111 to prevent the backflow of the refrigerant.

As mentioned above, although preferred embodiment of this invention was described in detail, the technical scope of this invention is not limited to the above-mentioned embodiment, It should be interpreted by a claim. At this time, one of ordinary skill in the art should consider that many modifications and variations are possible without departing from the scope of the present invention.

For example, it is not necessary to limit the installation position of the check valve 100 as described above, and the check valve 100 if the discharge chamber 24 pressure Pd and the crank chamber 86 pressure Pc can act. Note that the installation location of the can be changed in various ways.

Claims

In a variable displacement compressor in which a suction chamber, a discharge chamber and a crank chamber are formed,

A discharge passage connected to the discharge chamber;

A check valve mounted in the discharge passage to open and close the discharge passage by a pressure difference between a discharge chamber pressure and a crank chamber or suction chamber pressure;

A variable capacity compressor comprising a.
The method of claim 1,

The check valve,

A valve housing having a first refrigerant inlet through which the discharge chamber pressure acts and a refrigerant outlet connected to the first refrigerant inlet, and having an end portion opposed to the first refrigerant inlet;

A valve body for opening and closing the first refrigerant inlet;

A cover having a second refrigerant inlet through which the crank chamber or suction chamber pressure is applied and covering the open end of the valve housing; And

And a biasing member interposed between the cover and the valve body.
The method of claim 2,

The valve body,

A variable displacement compressor comprising a large diameter portion corresponding to the first refrigerant inlet and a small diameter portion corresponding to the second refrigerant inlet.
The method of claim 3, wherein

A variable capacity compressor characterized in that an elastic member is interposed between the large diameter portion and the small diameter portion.
The method of claim 4, wherein

The large diameter variable displacement compressor, characterized in that the mounting groove is formed in which the elastic member is seated.
The method of claim 3, wherein

And the check valve opens the discharge passage when the discharge chamber pressure is larger than the elastic force of the biasing member plus the pressure of the crank chamber or the suction chamber.
The method of claim 2,

The valve body,

A variable displacement compressor comprising a first valve body for opening and closing the first refrigerant inlet and a second valve body corresponding to the second refrigerant inlet.
The method of claim 7, wherein

The variable pressure compressor of claim 1, wherein the first valve body is formed with a hydraulic pressure portion to which the discharged backflow refrigerant acts, and the second valve body has a support portion inserted into the hydraulic pressure portion.
The method of claim 8,

The variable pressure type compressor, characterized in that the hydraulic pressure portion is provided with a guide portion is inserted to hold the initial position.
The method of claim 9,

The guide unit is a variable displacement compressor, characterized in that the inclined portion narrowing in the insertion direction.
The method of claim 9,

The variable displacement compressor, characterized in that the biasing member is seated on the radially outer side of the guide portion.
The method according to claim 1 or 2 or 7,

Capacitively variable compressor characterized in that the connection flow path for connecting the crank chamber or the suction chamber and the check valve.