KR20100065935A - Swash pate type compressor - Google Patents

Abstract

PURPOSE: A swash plate type compressor is provided to steadily inhale refrigerant regardless of the torque of a rotating drive shaft at high speed. CONSTITUTION: A swash plate type compressor(1000) comprises: housings(310,320); a cylinder block(100); a piston(200); a driving shaft(400); a swash plate(500); a valve plate(600); a rotary valve(R); a refrigerant intake hole which is formed in the cylinder block while being communicated with a refrigerant storage room of the housing and a swash plate room; a refrigerant inlet(410) which is formed in the driving shaft and is communicated with the refrigerant storage room; a refrigerant outlet(R1) which is formed in the rotary valve and is communicated with the refrigerant inlet; and a connecting hole(130) which is formed on the inner circumference of a combining hole which faces the refrigerant outlet and is respectively connected to a plurality of cylinder bores of the cylinder block.

Description

Swash plate type compressor {Swash pate type compressor}

The present invention relates to a swash plate compressor, and more particularly, to a swash plate compressor capable of efficiently sucking refrigerant flowing into the swash plate chamber through a cylinder block.

In general, a vehicle air conditioner is a device that maintains a temperature inside a car lower than an external temperature by using a refrigerant, and includes a compressor, a condenser, and an evaporator to configure a circulation cycle of the refrigerant.

The compressor is a device that compresses and pumps refrigerant, and is driven by engine power or a motor.

In the swash plate type compressor, which is a kind of reciprocating compressor, a disc shaped swash plate is installed on a drive shaft to which engine power is transmitted in a state in which the inclination angle is variable or fixed to the rotation of the drive shaft, and the circumference of the swash plate is rotated by the rotation of the swash plate. A plurality of pistons installed via a shoe along the structure is configured to suck, compress and discharge the refrigerant gas by linearly reciprocating the inside of the plurality of cylinder bores formed in the cylinder block.

Also, in the process of inhaling, compressing and discharging the refrigerant gas, a valve plate for intermitting the suction and discharge of the refrigerant gas is installed between the housing and the cylinder block.

Specifically, with reference to Figure 1 will be described in more detail the configuration of a conventional swash plate compressor.

As shown, the front housing (A10) is built in the front cylinder block (A20), the rear housing (A10a) is coupled to the front housing (A10) and built in the rear cylinder block (A20a), and the front and rear A plurality of pistons A50 reciprocating in the plurality of cylinder bores A21 formed in the cylinder blocks A20 and A20a, respectively, and a shoe A45 inclinedly coupled to the drive shaft A30 and installed on an outer circumference thereof. Valve plate (A60) installed between the swash plate (A40) and the front and rear housings (A10) (A10a) and the front and rear cylinder blocks (A20) (A20a) to be coupled to the piston (A50) via a). And an upper portion of the rear surface of the rear housing A10a to supply the refrigerant transferred from the evaporator during the suction stroke of the piston A50 into the compressor A1 and to compress the piston A50 during the compression stroke of the piston A50. ) Is composed of a muffler (A70) to discharge the refrigerant compressed inside the condenser .

A coolant discharge chamber A12 and a coolant suction chamber A11 are formed inside and outside the partition A13 in the front and rear housings A10 and A10a, respectively. Here, the coolant discharge chamber A12 is formed in the first discharge chamber A12a formed inside the partition A13 and outside the partition A13 and is partitioned from the coolant suction chamber A11 to form the first discharge chamber. It consists of the 2nd discharge chamber A12b which communicates with A12a and the discharge hole A12c. Accordingly, the refrigerant in the first discharge chamber A12a passes through the small diameter discharge hole A12c and moves to the second discharge chamber A12b. As a result, the pulsation pressure due to the periodic suction of the refrigerant is attenuated. This can reduce vibration and noise.

On the other hand, the front and rear cylinder block (A20) so that the refrigerant supplied to the swash plate chamber (A24) provided between the front and rear cylinder blocks (A20, A20a) can flow to each of the refrigerant suction chamber (A11). A plurality of suction passages A22 are formed in A20a, and the second discharge chamber A12b of the front and rear housings A10 and A10a passes through the front and rear cylinder blocks A20 and A20a. It communicates with each other by the formed connection path A23. Therefore, the suction and compression of the refrigerant may be simultaneously performed in the bore A21 of the front and rear cylinder blocks A20 and A20a according to the reciprocating motion of the piston A50.

The conventional swash plate compressor configured as described above compresses the refrigerant through the following process.

The refrigerant supplied from the evaporator is sucked into the suction part of the muffler A70 and then supplied to the swash plate chamber A24 between the front and rear cylinder blocks A20 and A20a through the refrigerant suction port A71, and the swash plate chamber The refrigerant supplied to A24 flows into the refrigerant suction chamber A11 of the front and rear housings A10 and A10a along the suction passage A22 formed in the front and rear cylinder blocks A20 and A20a. do.

Thereafter, the suction lead valve is opened during the suction stroke of the piston A50, so that the refrigerant in the refrigerant suction chamber A11 is sucked into the cylinder bore A21 through the refrigerant suction hole of the valve plate A60. . When the piston A50 is compressed, the refrigerant inside the cylinder bore A21 is compressed, and the discharge lead valve is opened, and the refrigerant flows through the refrigerant discharge hole of the valve plate A60. A10a flows to the first discharge chamber A12a. The refrigerant flowing into the first discharge chamber A12a is discharged to the discharge portion of the muffler A70 through the refrigerant discharge port A72 of the muffler A70 via the second discharge chamber A12b and then flows to the condenser. .

Meanwhile, the refrigerant compressed in the cylinder bore A21 of the front cylinder block A20 is discharged to the first discharge chamber A12a of the front housing A10 and then flows to the second discharge chamber A12b. Along the connection passage A23 formed in the front and rear cylinder blocks A20 and A20a, the second discharge chamber A12b of the rear housing A10a flows to the refrigerant discharge port A72 together with the refrigerant therein. Through the discharge portion of the muffler A70 is discharged.

However, in the conventional compressor A1, the suction of the refrigerant is caused by a loss due to a suction resistance caused by a complicated internal refrigerant flow path and a loss due to elastic resistance of the suction lead valve during opening and closing of the valve plate A60. There was a problem that the volumetric efficiency is reduced.

Meanwhile, Korean Patent Publication No. 2007-19564 (compressor, hereinafter referred to as 'prior art') discloses a technique for reducing the loss caused by the elastic resistance of the suction lead valve.

The prior art relates to a compressor to which a suction shaft integrated suction drive valve without a suction lead valve is applied. The refrigerant allows the refrigerant to directly enter the cylinder bore through the inside of the drive shaft in order to reduce the loss caused by the suction resistance. will be.

Specifically, as shown in FIG. 2, the swash plate B160 is inclinedly coupled and a flow path B151 through which a refrigerant flows is formed therein, and the flow path B151 is disposed on the swash plate hub side to which the swash plate B160 is coupled. At least one suction port B152 is formed in communication with the drive shaft B150 having an outlet B153 formed at a position spaced from the suction port B152, and the drive shaft B150 is rotatably installed and the swash plate chamber B136. A plurality of cylinder bores B131 and B141 are provided at both sides, and the refrigerant sucked into the flow path B151 of the drive shaft B150 sequentially rotates each cylinder bore B131 and B141 when the drive shaft B150 rotates. Front and rear cylinder blocks (B130) and (B140) formed with suction passages (B132) and (B142) for communicating the shaft support holes (B133) and (B143) and the respective cylinder bores (B131) and (B141) to be sucked into The cylinder bore (B131) (B141) mounted on the outer circumference of the swash plate (B160) via a shoe and linked with the rotational movement of the swash plate (B160). Compressor comprising a plurality of pistons (B170) for reciprocating in the inside, and the front and rear housings (B110) (B120) coupled to both sides of the cylinder block (B130) (B140) and the discharge chamber is formed therein, respectively. Is disclosed.

According to the conventional compressor, the refrigerant introduced through the suction port (not shown) flows into the drive shaft B150 through the suction port B152 formed on the hub side of the swash plate B160, and then the drive shaft B150. It is configured to flow into the cylinder bores B131 and B141 via the flow path B151 formed in the interior thereof.

However, since the suction port of the drive shaft is formed on the swash plate hub side to suck the refrigerant in the swash plate chamber while the drive shaft rotates, the suction shaft has a sufficient suction flow rate due to the flow resistance caused by the centrifugal force. There was a problem that can not be.

In addition, there is a problem that the volumetric efficiency of the compressor is lowered due to the flow path resistance of the refrigerant remaining in the suction passage, thereby preventing a sufficient suction flow rate.

The present invention has been made to solve the above problems, an object of the present invention is to allow the refrigerant in the swash plate chamber to be sucked through the cylinder block and at the same time the swash plate that can be stably supplied in a sufficient amount of refrigerant suction To provide a compressor.

In addition, another object of the present invention is to provide a swash plate type compressor equipped with a rotary valve which can further improve the volumetric efficiency of the compressor by reducing the flow path resistance and suction loss of the refrigerant by the rotary valve.

The swash plate compressor of the present invention for achieving the above object, a housing, a cylinder block having a plurality of cylinder bores are formed and coupled to the housing, and a piston that is reciprocally received in the cylinder bore, respectively, A drive shaft rotatably installed relative to the housing and the cylinder block, a swash plate rotated by the drive shaft and interlocked with the piston, a valve plate interposed between the housing and the cylinder block, and rotated together with the drive shaft. A swash plate type compressor including a rotary valve rotatably installed on an inner surface of a coupling hole formed in the cylinder block, the swash plate type compressor comprising: a refrigerant suction hole formed in the cylinder block so as to communicate with the refrigerant storage chamber of the swash plate chamber and the housing; Coolant inlet formed in the drive shaft, the rotary valve And a communication hole connected to the plurality of cylinder bores on an inner circumferential surface of the coupling hole formed to be in communication with the coolant inlet and facing the coolant outlet.

In addition, the coolant inlet is formed at one end in the longitudinal direction of the drive shaft or the outer circumferential surface of the drive shaft, and a coolant delivery hole communicating the coolant inlet and the coolant discharge port is preferably formed along the longitudinal direction of the drive shaft.

The coolant inlet may be formed at one end and the outer circumferential surface of the drive shaft, and a coolant delivery hole communicating the coolant inlet and the coolant outlet may be formed along the longitudinal direction of the drive shaft.

On the other hand, the rotary valve is formed with a first discharge groove, the inner peripheral surface of the coupling hole is preferably formed with a second discharge groove corresponding to the first discharge groove.

In addition, it is preferable that two first discharge grooves are formed between the refrigerant discharge ports.

According to the sine-type compressor according to the present invention, since the refrigerant suction hole for sucking the refrigerant in the swash plate chamber is formed in the coupling hole of the cylinder block, the refrigerant suction can be stably sucked regardless of the rotational force of the driving shaft rotating at high speed. There is an effect that can greatly reduce the loss by.

In addition, the rotary valve is formed with first and second discharge grooves for bypassing the refrigerant remaining in the communication hole of the cylinder bore during the compression stroke of the piston, so that the refrigerant supplied back into the cylinder bore after the compression stroke is not inhaled. You can move smoothly inside it.

The second discharge groove is formed in the cylinder block.

The second discharge groove is preferably formed in a circular shape continuous to the cylinder block.

Preferably, the cross-sectional area of each of the first discharge grooves is formed differently.

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

Prior to the description, the swash plate compressor 1000 according to the present invention has been applied to the embodiment of the double-headed piston compressor, but is not necessarily limited to the double-headed piston compressor can also be applied to a conventional double-headed piston compressor.

As shown in FIGS. 3 to 6, the swash plate compressor 1000 according to the present invention includes a cylinder block 100 having a plurality of cylinder bores 110, and a cylinder bore 110 of the cylinder block 100. Piston 200 which is accommodated in the reciprocating motion respectively, the front and rear housings 310 and 320 to be hermetically coupled to the front and rear of the cylinder block 100, respectively, the front housing 310 and the cylinder block ( A drive shaft 400 rotatably installed with respect to 100, a swash plate 500 interlocked with the drive shaft 400 and the piston 200, and the cylinder block 100 with the front and rear housings 310 and 320; It consists of a valve plate 600 interposed between.

Since the configuration is the same as the prior art of FIG. 1A described above, description of the overlapping configuration will be omitted and only the configuration having a difference will be described.

First, as shown in FIG. 3, the cylinder block 100 is interposed between the front and rear housings 310 and 320, and a plurality of cylinder bores 110 reciprocating therein are formed therein. do.

In particular, the cylinder block 100 is provided with a coupling hole 120, the rotary valve (R) is provided in the coupling hole 120 is free to slide rotation. The rotary valve R is formed in the drive shaft 400 itself.

In addition, as illustrated in FIGS. 3 and 4, a communication hole 130 for supplying refrigerant to each of the plurality of cylinder bores 110 is provided on the inner circumferential surface of the coupling hole 120 facing the outer circumferential surface of the rotary valve R. In addition to this being formed, a refrigerant suction hole 140 communicating from the swash plate chamber 101 to the housings 310 and 320 is formed.

The refrigerant suction hole 140 is disposed between the adjacent cylinder bores (110, 110) is effective for the refrigerant suction. Strictly, the refrigerant suction hole 140 may be disposed one by one between the neighboring communication holes (130, 130).

In addition, a coolant delivery hole 420 is formed in the drive shaft 400 in the longitudinal direction, and a coolant inlet 410 is formed to communicate with the coolant delivery hole 420, and the coolant inlet 410 is the coolant. Passing through the suction hole 140 serves to deliver the refrigerant contained in the refrigerant storage chamber (P1) to be described later to the rotary valve (R).

In addition, the coolant inlet 410 may be formed from one end portion in the longitudinal direction of the drive shaft 400 or may be formed on an outer circumferential surface of the drive shaft 400.

The refrigerant suction hole 140 and the refrigerant inlet 410 communicate with each other by the refrigerant storage chambers P1 formed in the front and rear housings 310 and 320.

Therefore, the suction refrigerant is the swash plate chamber 101, the refrigerant suction hole 140, the refrigerant storage chamber (P1), the refrigerant inlet 410, the refrigerant transfer hole 420, the rotary valve (R), the communication hole 130 and the cylinder It is compressed after passing through the bore 110 sequentially.

On the other hand, the rotary valve (R) is preferably formed integrally with the drive shaft 400 by processing the outer diameter of the drive shaft (400).

This may not only omit the process of separately manufacturing the rotary valve R and assembling it back to the drive shaft 400, but also reduce the friction between the rotary valve R and the drive shaft 400. To provide.

The configuration of the rotary valve (R) adopted in the embodiment of the present invention is as follows.

The rotary valve (R) is formed on the drive shaft 400, the one side of the outer circumferential surface of the cylinder suction hole 140 and the refrigerant flowed into the refrigerant storage chamber (P1) of the cylinder block 100 directly cylinder bore (110) And a refrigerant discharge port R1 for discharging while being in communication with each other.

The outer circumferential surface of the rotary valve R and the inner circumferential surface of the coupling hole 120 of the cylinder block 100 communicate with each other to remove high-pressure residual gas in the communication hole 130 of the cylinder bore 110. The first discharge grooves R2 and R3 and the second discharge groove 190 are formed.

The first discharge grooves R2 and R3 are formed with the refrigerant discharge holes R1 formed in the drive shaft 400 interposed therebetween. In this case, one side of the first discharge groove (R2) serves to suck the refrigerant in the communication hole 130, the first discharge groove (R3) formed on the other side residual gas passing through the second discharge groove (190) It serves to discharge to the expanded cylinder bore 110 through the communication hole 130 opposite.

The second discharge groove 190 is formed in a continuous circular shape recessed to a predetermined depth along the circumference of the inner peripheral surface of the coupling hole (120). Here, the second discharge groove 190 serves as an intermediate passage for supplying the high-pressure residual gas moved from the one side first discharge groove R2 to the other side first discharge groove R3.

Accordingly, the refrigerant remaining in the communication hole 130 may be configured to allow the first discharge groove R2, the second discharge groove 190, and the first discharge groove R3 on the other side of the driving shaft 400 to rotate. After passing sequentially, it is discharged to the expanded cylinder bore 110 through the communication hole 130 on the opposite side.

The first discharge groove R2 and the second discharge groove 190 are trapped in the communication hole 130 to suck the refrigerant again after the piston 200 that sucks and compresses the refrigerant reaches a top dead center. By preventing the suction loss caused by the residual pressure of the high pressure serves to smoothly suck the refrigerant into the cylinder bore (110).

According to this configuration, the refrigerant introduced through the refrigerant suction hole 140 of the cylinder block 100 is moved to the refrigerant storage chamber P1 of the front and rear housings 310 and 320, and then the refrigerant in the refrigerant storage chamber P1. Reflows through the refrigerant inlet 410 of the drive shaft 200 and the introduced refrigerant is discharged to the cylinder bore 110 through the refrigerant transfer hole 420, the refrigerant discharge port (R1) and the communication hole 130.

If necessary, the cross-sectional area of the first discharge groove (R2) may be formed differently.

Hereinafter, the refrigerant suction structure of the swash plate compressor according to the embodiment of the present invention will be described with reference to FIGS. 3 to 6.

First, when the drive shaft 400 of the compressor 1000 is rotated by receiving power, the swash plate 500 is rotated, the plurality of pistons 200 in conjunction with the rotational movement of the swash plate 500 is the cylinder block ( The suction and compression of the refrigerant is repeatedly performed while reciprocating inside the cylinder bore 110 of 100).

Subsequently, looking at the suction structure of the refrigerant flowing into the cylinder bore 110 in detail, the refrigerant introduced into the swash plate chamber 101 from the evaporator (not shown) is a cylinder block (B) by the suction stroke of the piston 200. It is introduced into the refrigerant suction hole 140 of 100. The refrigerant moved in the axial direction through the refrigerant suction hole 140 moves to the refrigerant storage chamber P1 of the front and rear housings 310 and 320.

Thereafter, the refrigerant stored in the refrigerant storage chamber P1 is sucked into the cylinder bore 110 through the refrigerant discharge port R1 of the rotary valve R through the refrigerant inlet 410 and the refrigerant transfer hole 420.

The coolant inlet 410 is formed near both ends of the drive shaft 400, and the coolant is continuously sucked into the cylinder bore 110 through the coolant inlet 410.

Meanwhile, since the first discharge grooves R2 and R3 and the second discharge groove 190 are formed in the coupling hole 120 and the rotary valve R, after the compression stroke of the piston 200 reaches the top dead center. The communication holes 130 of the cylinder bore 110 communicate with each other, and the refrigerant remaining in the cylinder bore is discharged to the expanded cylinder bore 110 through the opposite communication hole 130 so that the suction of the refrigerant can proceed smoothly. do.

Thereafter, the refrigerant compressed in the cylinder bore 110 is discharged into the refrigerant discharge chamber P2 of the front and rear housings 310 and 320.

In addition, it is also possible to form a single suction structure by applying to the structure without the refrigerant storage chamber (P1) separately.

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 the claim. At this time, those of ordinary skill in the art should consider that many modifications and variations are possible without departing from the scope of the present invention.

Representatively, the coolant inlet 410 may be formed only at one end or the outer circumferential surface of the drive shaft 400.

In the drawing, the coolant inlet 410 is formed on the outer circumferential surface and the end of the drive shaft 400, but both may be formed on the outer circumferential surface or the end.

1 is a front sectional view and a side sectional view showing the configuration of a conventional swash plate type compressor.

2 is a cross-sectional view showing a swash plate compressor equipped with a rotary valve according to the prior art.

3 is a cross-sectional view showing a swash plate compressor according to the present invention.

4 is a perspective view showing a cylinder block of the swash plate compressor according to the present invention.

5 is a perspective view showing a state in which the drive shaft and the swash plate according to the present invention is coupled.

6 is a cross-sectional view showing a residual gas discharge structure of the swash plate compressor according to the present invention.

* Description of symbols on main parts of the drawings *

1000-Swash plate compressor 100-Cylinder block

101-Throttle Room 110-Cylinder Bore

120-Coupling Hole 130-Communication Hole

140-Refrigerant suction hole 200-Piston

310-front housing 320-rear housing

400-Drive shaft 410-Refrigerant inlet

500-Swash Plate 600-Valve Plate

R-Rotary Valve R1-Refrigerant Discharge Outlet

R2, R3-First discharge groove 190-Second discharge groove

P1-Refrigerant Storage Room P2-Refrigerant Discharge Room

Claims (8)

A housing, a cylinder block having a plurality of cylinder bores formed therein, coupled to the housing, a piston accommodated reciprocally in the cylinder bore, a drive shaft rotatably installed with respect to the housing and the cylinder block, and the drive shaft The rotary valve is rotated by the swash plate, the valve plate interposed between the housing and the cylinder block, and the rotary valve is formed to rotate together with the drive shaft and rotatably installed on the inner surface of the coupling hole formed in the cylinder block In the swash plate compressor comprising: A refrigerant suction hole formed in the cylinder block to communicate with the swash plate chamber and the refrigerant storage chamber of the housing; A refrigerant inlet formed in the drive shaft so as to communicate with the refrigerant storage chamber; A coolant discharge port formed in the rotary valve and communicating with the coolant inlet port; And And a communication hole connected to the plurality of cylinder bores on an inner circumferential surface of the coupling hole facing the refrigerant discharge port. The method of claim 1, The refrigerant inlet is formed in one end of the longitudinal direction of the drive shaft or the outer peripheral surface of the drive shaft, the refrigerant delivery hole for communicating the refrigerant inlet and the refrigerant discharge port is formed along the longitudinal direction of the drive shaft. The method of claim 1, The refrigerant inlet is formed on one end and the outer peripheral surface of the drive shaft, respectively, the swash plate type compressor, characterized in that the refrigerant delivery hole communicating the refrigerant inlet and the refrigerant discharge port is formed along the longitudinal direction of the drive shaft. The method according to any one of claims 1 to 3, The rotary valve is formed with a first discharge groove, the swash plate compressor, characterized in that the inner circumferential surface of the coupling hole is formed with a second discharge groove corresponding to the first discharge groove. The method of claim 4, wherein The swash plate type compressor, characterized in that the first discharge groove is formed between two refrigerant outlets. The method of claim 4, wherein And the second discharge groove is formed in the cylinder block. The method of claim 4, wherein The second discharge groove is a swash plate compressor, characterized in that formed in a continuous circular shape on the cylinder block. The method of claim 5, Swash plate compressor, characterized in that the cross-sectional area of each of the first discharge groove is formed differently.

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