KR20130092876A - Swash plate type variable capacity compressor - Google Patents

Abstract

PURPOSE: A variable capacity swash plate type compressor is provided to reduce the suction pulsation of refrigerant which passes through a suction check valve by improving a structure of a suction flow path on which the suction check valve is installed, thereby implementing noise reduction. CONSTITUTION: A variable capacity swash plate type compressor includes a front housing which is connected to the front side of a cylinder block (100); a rear housing (300) which has a suction chamber (310) by being combined with the rear side of the cylinder block; a suction flow path (350) which connects the suction chamber with a suction port (370); and a suction check valve (700). The suction check valve is provided on the refrigerant discharge side of the suction flow path, and formed to have a window (711) through which refrigerant is flowed on the circumferential surface; and a part of the area on which the window is formed is installed to be protruded toward the inside of the suction chamber. An expanded part (600) which has a space expanded more than any other parts is additionally formed on the area, where the suction check valve is installed on the inner circumferential surface of the suction flow path of the rear housing.

Description

[0001] The present invention relates to a swash plate type variable capacity compressor,

The present invention relates to a variable displacement swash plate compressor, and more particularly, to reduce the suction pulsation during the refrigerant flow from the suction port to the suction chamber, thereby reducing the noise and vibration caused by excessive suction pulsation. The present invention relates to a variable displacement swash plate compressor according to a new form.

In general, the compressor used in the air conditioning system of the vehicle takes the refrigerant evaporated from the evaporator and transfers it to the condenser by making it easy to liquefy at high temperature and high pressure.

Among the compressors of the automotive air conditioning system, the swash plate type compressor has a structure in which the swash plate is rotated while the drive shaft is rotated by the driving force of the engine, and the piston is reciprocated in accordance with the rotation of the swash plate to compress the refrigerant. The swash plate of the swash plate type compressor is configured to be capable of changing the inclination angle according to the compression capacity.

1 is a cross-sectional view of a conventional variable displacement swash plate type compressor.

The conventional variable displacement swash plate type compressor includes a cylinder block 10 in which a plurality of cylinder bores 11 are radially formed and a crank chamber 21 formed in front of the cylinder block 10 A front housing 20 and a rear housing 30 coupled to the rear of the cylinder block 10 to form a suction chamber 31 and a discharge chamber 33. [

At this time, the cylinder bores 11 are accommodated in the piston 42, respectively, the valve assembly 50 for controlling the flow of the refrigerant is installed between the cylinder block 10 and the rear housing 30.

In addition, the suction chamber 31 formed in the rear housing 30 is configured to communicate with the suction port 37 through the suction passage 35.

In addition, a drive unit for reciprocating the piston 42 is installed inside the crank chamber 21.

The drive unit is installed penetrating through the center of the front housing 20 and the cylinder block 10, the drive shaft 41 is rotated by the driving force transmitted from the engine, and coupled to the drive shaft 41 in the crank chamber 21 And a rotor 43 that rotates together with the drive shaft 41, and a swash plate 44 that is hinged to the rotor 43 and has a variable inclination angle.

At this time, the swash plate 44 is connected to each piston 42 through the shoe 45, so that each piston 42 reciprocates in the cylinder bore 11 by the rotation of the swash plate 44 While compressing the refrigerant in the cylinder bore (11).

On the other hand, the variable displacement swash plate compressor according to the prior art described above, each cylinder bore 11 as the speed of the refrigerant flowing into the cylinder bore 11 from the suction chamber 31 during the compression operation of the refrigerant is irregular. In each suction stroke, the refrigerant pressure distribution in the suction chamber 31 became nonuniform, causing irregular waves, that is, suction pulsations. As a result, noise caused by the suction pulsations was continuously generated during the compression operation of the compressor. There is a problem that has occurred.

In addition, the pulsation generated by the compressor as described above is provided to the heat exchanger forming the air conditioning system of the vehicle through various piping together with the discharge pulsation generated during the discharge, causing additional problems such as vibration of the heat exchanger. .

In the related art, the suction check valve 70 is additionally provided in the suction passage 35 through which the refrigerant is transferred from the suction port 37 to the suction chamber 31. 37) to prevent backflow and reduce noise and vibration.

2, the suction check valve 70 is installed at a portion where the suction passage 35 communicates with the suction chamber 31, and includes a valve case 71, a core 72, (73).

At this time, a window 71a is formed on the circumference of the valve case 71, and the core 72 is configured to selectively open the window 71a while being elastically moved in the valve case 71.

However, the above-described suction check valve 70 only serves to reduce noise and vibration due to the flow of the refrigerant discharged backward from the suction chamber 31 toward the suction port 37 when the compressor is stopped. The noise and vibration reduction effect of the suction pulsation during the operation of the compressor was not provided, and thus, despite the additional provision of the suction check valve 70, the prevention of the problem due to the suction pulsation of the refrigerant was not sufficiently performed. It was.

The present invention has been made to solve the various problems according to the prior art described above, the object of the present invention is to provide a suction pulsation of the refrigerant passing through the suction check valve through the structural improvement of the suction flow path is installed suction suction valve It is to provide a variable displacement swash plate compressor according to a new form that can be attenuated, thereby reducing the noise.

According to the variable displacement swash plate type compressor of the present invention for achieving the above object, a front housing coupled to the front of the cylinder block, a rear housing having a suction chamber coupled to the rear of the cylinder block, and a suction port for the suction chamber. And a suction flow passage communicating with the suction flow passage, and a suction flow check valve provided on the refrigerant discharge side of the suction flow passage to form a window through which the refrigerant flows, and a part of the window formed portion protrudes into the suction chamber. In the variable displacement swash plate type compressor, an extension part having an enlarged space is further formed at a portion of the suction flow path of the rear housing in which the suction check valve is installed.

Here, the expansion portion is characterized in that formed on the portion of the inner circumferential surface of the suction flow path is located the window of the suction check valve.

The suction chamber of the rear housing further includes an extension portion protruding from the suction passage into the suction chamber to surround a part of the suction check valve protruding into the suction chamber. The extension portion is also formed on the inner peripheral surface of the extension portion .

The recess depth of the extension is in the range of 0.35 mm to 1.6 mm, and the length of the extension is in the range of 14.5 mm to 21.0 mm.

Further, the extension portion is formed to communicate with the inside of the suction chamber.

In the variable capacity swash plate type compressor of the present invention as described above, an expansion portion is additionally formed at a position where the window of the suction check valve in the suction passage is located, the refrigerant that flows into the suction passage and passes through the suction check valve, The suction pulsation can be attenuated and the noise can be reduced.

In particular, since the expansion portion is formed by changing the shape of a part of the flow path rather than adding a separate component for reducing noise, there is also an effect that the assembly operation or the manufacturing can be easily performed.

1 is a cross-sectional view illustrating an internal structure of a conventional variable capacity swash plate type compressor
Figure 2 is an enlarged cross-sectional view showing the main portion to explain the structure and process of the refrigerant is sucked into the suction chamber of a conventional general variable displacement swash plate type compressor
3 is a cross-sectional view illustrating the internal structure of a variable displacement swash plate compressor according to an embodiment of the present invention.
FIGS. 4 and 5 are enlarged cross-sectional views illustrating a structure in which a suction check valve of a variable capacity swash plate type compressor is installed and a suction process of a refrigerant according to a preferred embodiment of the present invention;
6 to 9 are enlarged cross-sectional views illustrating a structure in which a suction check valve of a variable capacity swash plate type compressor is installed and a suction process of a refrigerant according to another preferred embodiment of the present invention;

Hereinafter, a preferred embodiment of the variable displacement swash plate compressor of the present invention will be described with reference to FIGS. 3 and 9.

Attached Figure 3 shows the internal structure of the variable displacement swash plate compressor of the present invention, according to the variable displacement swash plate compressor of the present invention largely the cylinder block 100, the front housing 200, the rear housing 300, the suction port 370, the suction check valve 700, and the expansion part 600 are provided.

This will be described in more detail below for each configuration.

First, the cylinder block 100 is a portion that forms the exterior of the compressor together with the front housing 200 and the rear housing 300.

The cylinder block 100 has a plurality of cylinder bores 110 are formed through the radial direction on the basis of the hollow portion in the center, the hollow portion is provided to the center bore 120, the drive shaft 410 is installed. .

Inside the respective cylinder bores 110, the piston 420 is installed so as to enable a linear reciprocating motion.

Next, the front housing 200 is coupled to the front of the cylinder block 100 to form a crank chamber 210. The rear housing 300 is coupled to the rear of the cylinder block 100, (310) and discharge chamber (330) are formed.

A suction port 370 for receiving a refrigerant from the outside is formed in the rear housing 300 and the refrigerant flows between the suction port 370 and the suction chamber 310 by the suction flow path 350, .

Next, the driving unit is installed inside the crank chamber 210 to linearly reciprocate the piston 420 in the cylinder bore 110.

The driving unit receives a driving force of the engine from the pulley 2, the drive shaft 410 is rotated, and the rotor 430 is coupled to the drive shaft 410 in the crank chamber 210 to rotate with the drive shaft 410 And, the swash plate hub 460 rotatably coupled to the drive shaft 410, and the swash plate 440 is rotated together with the swash plate hub 460 while its inclination angle is variably installed in the swash plate hub 460 It is configured to include).

Here, a hinge arm 431 protrudes from a wall surface of the outer wall of the rotor 430 facing the swash plate 440, and a swash plate arm overlapping the hinge arm 431 on the swash plate hub 460. 461 is formed to protrude, and the hinge arm 431 and the swash plate arm 461 are hinged to each other.

Next, the valve assembly 500 is a portion for controlling the refrigerant flow between the cylinder bore 200 of the cylinder block 100 and the suction chamber 310 and the discharge chamber 330 of the rear housing 300.

Next, the suction check valve 700 is installed in the suction passage 350 of the rear housing 300 to block the refrigerant in the suction chamber 310 from flowing back to the suction port 370.

The suction check valve 700 includes a valve case 710, a valve cap 740, a core 720, and an elastic member 730 as shown in FIG. 4.

Here, the valve case 710 is a portion constituting the body of the suction check valve 700, one end (right side in the drawing) is opened and the other end (left side in the drawing) is closed, the inside is a cylindrical shape having an empty space Is formed.

At this time, a plurality of windows 711 are formed on the circumferential surface of the valve case 710, and the window 711 is connected to the inner space of the valve case 710 and the suction chamber 310 of the rear housing 300 And the space in the space is communicated with each other.

The valve case 710 is installed such that one end of the valve case 710 is opened in the suction passage 350 and the closed end of the valve case 710 is partially protruded into the suction chamber 310 through the suction passage 350, The valve case 710 is installed such that a part of the window 711 formed in the valve case 710 is positioned within the suction passage 350.

And, the valve cap 740 is coupled to the open end of the valve case 710 to prevent the core 720 in the valve case 710 is separated from the open end of the valve case 710. Do it.

In this case, an inlet hole 741 is formed at the central portion of the valve cap 740 to guide the refrigerant sucked from the suction port 370 into the valve case 710.

The core 720 is configured to selectively open and close the window 711 formed in the valve case 710 while being elastically movably installed in the valve case 710 by the elastic member 730.

At this time, the core 720 is positioned in the suction passage 350 among the respective portions of the window 711 formed in the valve case 710 while being in close contact with the valve cap 740 in a no-load state in which the refrigerant is not sucked The core 720 is moved to the other end of the valve case 710 so that a portion of the window 711 located in the suction passage 350 And the portion communicating with the suction chamber 310 are simultaneously opened.

Next, the expansion part 600 is a portion for attenuating the suction pulsation of the refrigerant, and as shown in FIG. 4, in the valve case 710 of the suction check valve 700 of the inner circumferential surface of the suction flow path 350. A part of the formed window 711 is formed to have an extended space at a location where the position is located.

That is, when the refrigerant flowing through the suction check valve 700 through the suction port 370 passes through the window 711 of the suction check valve 700, attenuation of the suction pulsation through expansion of the discharge space So that it is possible to flow into the suction chamber 310 so that noise due to the suction pulsation can be reduced.

In addition, the expansion part 600 is formed to communicate with the inside of the suction chamber 310. If the expansion part 600 is formed in a closed space blocked from the suction chamber 310, the attenuation effect of the suction pulsation is reduced by the influence of the refrigerant remaining in the expansion part 600 and remaining. The expansion unit 600 is formed in an open space which is always in communication with the suction chamber 310 so that the suction pulsation of the newly sucked refrigerant can be smoothly attenuated.

Meanwhile, the recessed depth H and the length L of the expansion portion 600 of the variable capacity swash plate type compressor according to the embodiment of the present invention are set differently according to the operation conditions of the compressor.

For example, if the recess depth H of the expansion part 600 is relatively increased and the length L thereof is increased, the effect of reducing the pulse pressure during the operation of the compressor in the 5-fold drainage state is relatively high. However, Is relatively low.

On the other hand, if the depth of the extension part 600 is relatively increased and the length thereof is increased, the effect of decreasing the pulse pressure during the operation of the compressor in the 5-fold drainage state is relatively low. However, Is relatively high.

The recessed depth H of the extension portion 600 is in the range of 0.35 mm to 1.6 mm and the length L of the expanded portion 600 is designed in the range of 14.5 mm to 21.0 mm .

In the following, the operation of the variable displacement swash plate compressor according to the embodiment of the present invention described above will be described.

First, when the operation control of the compressor is generated, the drive shaft 410 is rotated by the driving force of the engine, and the swash plate connected to the rotor 430 while the rotor 430 is also rotated by the rotation of the drive shaft 410. 440 is rotated.

When the swash plate 440 is rotated, the rotation of the swash plate 440 is transmitted to each of the pistons 420 through the shoe 450, thereby causing the piston 420 to move in the cylinder bore 110 So that the refrigerant sucked into the cylinder bore 110 is compressed.

At this time, the refrigerant is introduced into the suction port 370 and then flows along the suction flow path 350 to be provided into the suction chamber 310 of the rear housing 300, and then continues to pass through the valve assembly 500 to the cylinder. Provided into bore 110.

In particular, the refrigerant flowing along the suction flow path 350 while the suction flow of the refrigerant proceeds passes through the suction check valve 700 and the expansion part 600 provided in the suction flow path 350. In this process, the suction pulsation of the refrigerant is attenuated.

That is, the refrigerant passes through the inflow hole 741 of the valve cap 740 constituting the suction check valve 700, flows into the valve case 710, and the inflow pressure of the refrigerant causes the core 720 to be attached The window 711 is gradually opened while being moved to the other end of the valve case 710 as shown in FIG. 5, and at the moment when the portion of the window 711, which is located in the suction passage 350, The refrigerant flowing into the valve case 710 flows into the expansion part 600 formed in the suction path 350. In this process, the expansion part 600 functions as a substantial muffler, The suction pulsation is attenuated.

When the core 720 is completely moved to the other end of the valve case 710 and opened to the window 711 located in the suction chamber 310, Is introduced into the suction chamber 310 through the valve assembly 711 and is introduced into the cylinder bore 110 through the valve assembly 500.

Thereafter, the refrigerant introduced into the cylinder bore 110 by the operation of the piston 420 in the cylinder bore 110 is compressed.

The refrigerant compressed in the cylinder bore 110 is discharged to the discharge chamber 330 of the rear housing 300 by the selective operation of the valve assembly 500. The suction, compression, and discharge processes of the refrigerant are sequentially and repeatedly performed to continuously compress the refrigerant.

As a result, the variable displacement swash plate compressor of the present invention can attenuate the suction pulsation of the refrigerant passing through the suction check valve 700 by additionally providing the extension 600 in the suction passage 350 to reduce noise. It is possible to achieve this, and thereby has the advantage of being able to reduce the starting noise of the entire compressor.

On the other hand, Figures 6 and 7 attached show a portion in which the suction check valve 700 of the variable displacement swash plate compressor according to another embodiment of the present invention is installed.

Another embodiment of the present invention proposes extending the region where the expansion portion 600 is formed to further enhance the damping effect on the suction pulsation of the refrigerant.

That is, the suction pulsation of the refrigerant is provided to the suction chamber 310 in a state where the suction pulsation of the refrigerant is attenuated as much as the extension length of the extension 600.

To this end, in another embodiment of the present invention, the suction check protrudes into the suction chamber 310 while protruding into the suction chamber 310 from the suction passage 350 in the suction chamber 310 of the rear housing 300. An extension part 390 surrounding a part of the valve 700 is further formed, and the extension part 600 is extended to the inner circumferential surface of the extension part 390.

Of course, even in this case, it is preferable that the expansion part 600 is formed to communicate with the inside of the suction chamber 310. This is because the refrigerant flowing through the window 711 is delayed by the extension length of the extension part 390 so that the refrigerant introduced into the extension part 600 may be provided directly into the suction chamber 310. By doing so, it is possible to prevent the delay of the suction time of the refrigerant.

In addition, the recessed depth of the enlarged portion 600 may be relatively shallow as shown in FIGS. 8 and 9, which is the case in the case of a 5-fold drainage during operation of the compressor, or 10 It is designed differently according to the effect of reducing the pulse pressure at drainage.

As such, in the variable displacement swash plate compressor according to the present invention, as the expansion part 600 is additionally formed at a portion where the window 711 of the suction check valve 700 is located in the suction flow path 350, the suction flow path ( The refrigerant introduced into 350 and passing through the suction check valve 700 may have its suction pulsation attenuated, thereby reducing noise.

100. Cylinder Block 110. Cylinder Bore
120. Center bore 200. Front housing
210. Crankcase 300. Rear housing
310. Suction chamber 330. Discharge chamber
350. Suction channel 370. Suction port
390. Extension 410. Drive Shaft
420. Piston 430. Rotor
431. Hinge arm 440. Swash plate
450. Shoe 460. Saffan hub
461. Swaff arm 500. Valve assembly
600. Extension 700.Suction Check Valve
710.Valve case 711.Windows
720. Core 730. Elastic member
740. Valve cap 741. Inlet ball

Claims (5)

The front housing 200 coupled to the front of the cylinder block 100, the rear housing 300 is coupled to the rear of the cylinder block 100 having a suction chamber 310, and the suction port 310 to the suction port The suction passage 350 communicating with the 370 and a window 711 through which the refrigerant flows are formed on the circumferential surface of the suction passage 350, and the window 711 is formed on the circumferential surface thereof. In the variable displacement swash plate type compressor including a suction check valve 700 is installed to protrude into the suction chamber 310,
Variable portion type, characterized in that the expansion portion 600 having an expanded space than the other portion is further formed in the portion of the suction housing 350, the inner peripheral surface of the rear housing 300 is installed in the suction check valve 700 Swash plate compressor. The method of claim 1,
The expansion unit 600
Variable displacement type swash plate compressor, characterized in that formed on the portion of the inner circumferential surface of the suction flow path 350, the window 711 of the suction check valve 700 is located. The method of claim 1,
An extension that surrounds a portion of the suction check valve 700 protruding into the suction chamber 310 while protruding into the suction chamber 310 from the suction passage 350 in the suction chamber 310 of the rear housing 300. A portion 390 is further formed,
The expansion unit (600) is a variable displacement swash plate type compressor, characterized in that the extension is formed on the inner peripheral surface of the extension (390). The method of claim 1,
Wherein the recessed depth H of the extension portion 600 is in a range between 0.35 mm and 1.6 mm and the length L of the extension portion 600 is in a range between 14.5 mm and 21.0 mm. Type swash plate compressor. The method according to any one of claims 1 to 4,
The expansion unit 600 is a variable displacement swash plate type compressor, characterized in that formed in communication with the interior of the suction chamber (310).

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