CN113056608A

CN113056608A - Swash plate type compressor

Info

Publication number: CN113056608A
Application number: CN202080006269.4A
Authority: CN
Inventors: 柳俊夏; 徐旼皓; 孙殷基; 尹齐秀; 李炫雨; 郑裕澈; 崔炯寅
Original assignee: Hanon Systems Corp
Current assignee: Hanon Systems Corp
Priority date: 2019-01-25
Filing date: 2020-01-21
Publication date: 2021-06-29
Anticipated expiration: 2040-01-21
Also published as: KR20200092667A; CN113056608B; WO2020153705A1

Abstract

The present invention relates to a swash plate type compressor including: a housing having a bore, a suction chamber, a discharge chamber, and a crank chamber; a rotating shaft rotatably mounted to the housing; a swash plate rotating together with the rotary shaft; pistons that are linked with the swash plate, reciprocate inside the bores, and form compression chambers with the bores; a first discharge passage that guides the refrigerant in the crank chamber to the suction chamber; and a second discharge passage that branches off from the first discharge passage or bypasses the first discharge passage and guides the refrigerant in the crank chamber to the suction chamber. Therefore, the operation delay caused by the liquid refrigerant during the initial operation can be improved.

Description

Swash plate type compressor

Technical Field

The present invention relates to a swash plate type compressor, and more particularly, to a swash plate type compressor capable of adjusting an inclination angle of a swash plate by adjusting a pressure of a crank chamber provided with the swash plate.

Background

Conventionally, a compressor for compressing a refrigerant in a cooling system for a vehicle has been developed in various forms, the compressor having: a reciprocating type, a structure of compressing a refrigerant performs compression while performing a reciprocating motion; the rotary type, which performs compression while performing a rotational motion.

And, the reciprocating type includes: a crank type in which a driving force of a driving source is transmitted to a plurality of pistons using a crank, a swash plate type in which a driving force of a driving source is transmitted to a rotary shaft provided with a swash plate, and a wobble plate type using a wobble plate, the rotary type including: a vane rotary type using a rotating shaft and vanes, a scroll type using an orbiting scroll and a fixed scroll.

Here, the swash plate type compressor is a compressor that compresses a refrigerant by reciprocating pistons by a swash plate rotating with a rotary shaft, and in recent years, in order to improve the performance and efficiency of the compressor, the swash plate type compressor is a so-called variable displacement type compressor in which the discharge amount of the refrigerant is adjusted by adjusting the stroke of the pistons by adjusting the inclination angle of the swash plate.

Fig. 1 is a sectional view showing a conventional swash plate type compressor of a variable displacement type.

Referring to fig. 1, a conventional swash plate type compressor includes: a housing 100 having a hole 116, a suction chamber S1, a discharge chamber S3, and a crank chamber S4; a rotating shaft 200 rotatably supported by the housing 100; a swash plate 300 which rotates inside the crank chamber S4 in conjunction with the rotary shaft 200; a piston 400 reciprocating inside the bore 116 in conjunction with the swash plate 300 and forming a compression chamber S2 with the bore 116; a valve mechanism 500 for communicating and blocking the suction chamber S1 and the discharge chamber S3 with the compression chamber S2; and an inclination adjustment mechanism for adjusting an inclination angle of the swash plate 300 with respect to the rotary shaft 200 (an angle between the rotary shaft 200 of the swash plate 300 and a normal line of the swash plate 300 with reference to a rotation center of the swash plate 300).

The tilt adjusting mechanism includes: an inflow passage (not shown) for guiding the refrigerant in the discharge chamber S3 to the crank chamber S4; and a discharge passage 800 for guiding the refrigerant in the crank chamber S4 to the suction chamber S1.

A pressure regulating valve (not shown) that regulates the amount of refrigerant flowing from the discharge chamber S3 into the inflow channel (not shown) is formed in the inflow channel (not shown).

The discharge passage 800 is formed with an orifice 810 for depressurizing the fluid passing through the discharge passage 800.

In the conventional swash plate type compressor according to this structure, when power is transmitted from a driving source (e.g., an engine of a vehicle) (not shown) to the rotary shaft 200, the rotary shaft 200 and the swash plate 300 are rotated together.

The piston 400 converts the rotational motion of the swash plate 300 into a linear motion and reciprocates inside the bore 116.

When the piston 400 moves from the top dead center to the bottom dead center, the compression chamber S2 communicates with the suction chamber S1 through the valve mechanism 500 and shields the discharge chamber S3, and the refrigerant in the suction chamber S1 is sucked into the compression chamber S2.

When the piston 400 moves from the bottom dead center to the top dead center, the compression chamber S2 is shielded from the suction chamber S1 and the discharge chamber S3 by the valve mechanism 500, and the refrigerant in the compression chamber S2 is compressed.

When the piston 400 reaches the top dead center, the compression chamber S2 is shielded from the suction chamber S1 by the valve mechanism 500, communicates with the discharge chamber S3, and the refrigerant compressed in the compression chamber S2 is discharged to the discharge chamber S3.

Here, in the conventional swash plate type compressor, the amount of refrigerant flowing from the discharge chamber S3 into the inflow path (not shown) is adjusted by the pressure regulating valve (not shown) according to a required amount of refrigerant to adjust the pressure of the crank chamber S4, and the pressure of the crank chamber S4 applied to the piston 400 is adjusted to adjust the stroke of the piston 400 and the inclination angle of the swash plate 300 to adjust the amount of refrigerant discharged.

That is, when the refrigerant discharge amount needs to be decreased, the amount of refrigerant flowing from the discharge chamber S3 into the inflow channel (not shown) is increased by the pressure regulating valve (not shown), and the amount of refrigerant flowing into the crank chamber S4 through the inflow channel (not shown) is increased, so the pressure in the crank chamber S4 is increased. Here, the refrigerant in the crank chamber S4 is discharged to the suction chamber S1 through the discharge passage 800, but the amount of refrigerant flowing from the discharge chamber S3 into the suction chamber S1 through the inflow passage (not shown) is greater than the amount of refrigerant discharged from the crank chamber S4 into the suction chamber S1 through the discharge passage 800, and thus the pressure of the crank chamber S4 increases. Accordingly, the pressure applied to the crank chamber S4 of the piston 400 is increased, the stroke of the piston 400 is decreased, the inclination angle of the swash plate 300 is decreased, and the discharge amount of refrigerant is decreased.

On the other hand, when the required amount of refrigerant discharge is increased, the amount of refrigerant flowing from the discharge chamber S3 into the inflow channel (not shown) is decreased by a pressure regulating valve (not shown), and the amount of refrigerant flowing into the crank chamber S4 through the inflow channel is decreased, so that the pressure of the crank chamber S4 is decreased. Here, even if the refrigerant in the discharge chamber S3 flows into the crank chamber S4 through the inflow passage (not shown), the pressure in the crank chamber S4 is reduced because the amount of refrigerant discharged from the crank chamber S4 to the suction chamber S1 through the discharge passage 800 is greater than the amount of refrigerant flowing from the discharge chamber S3 to the crank chamber S4 through the inflow passage (not shown). Accordingly, the pressure applied to the crank chamber S4 of the piston 400 is reduced, thereby increasing the stroke of the piston 400, increasing the inclination angle of the swash plate 300, and increasing the discharge amount of refrigerant.

Here, in explaining the principle of adjusting the refrigerant discharge amount, the inclination angle of the swash plate 300 is mainly formed by the piston 400 by a moment difference due to a pressure difference obtained by subtracting the pressure of the crank chamber S4 from the pressure of the compression chamber S2 acting on the piston 400, and the smaller the pressure of the crank chamber S4 is, the larger the inclination angle of the swash plate 300 is, the larger the stroke of the piston 400 is, and the larger the refrigerant discharge amount is. On the other hand, as the pressure of the crank chamber S4 increases, the inclination angle of the swash plate 300 decreases, the stroke of the piston 400 decreases, and the refrigerant discharge amount decreases.

On the other hand, when the refrigerant in the crank chamber S4 flows into the suction chamber S1 through the discharge passage 800, the pressure is reduced to the level of suction pressure through the orifice 810, thereby preventing the pressure in the suction chamber S1 from increasing.

However, such a conventional swash plate compressor has a problem in that operation is delayed by the liquid refrigerant at the initial operation. That is, when the swash plate compressor is left for a long time, the liquid refrigerant is accumulated in the inside of the housing 100, and the liquid refrigerant is not compressible, thereby causing a factor of preventing the pressure generation in the crank chamber S4, which may cause an operation delay at the time of initial operation.

Disclosure of Invention

Technical problem to be solved

Accordingly, an object of the present invention is to provide a swash plate type compressor capable of improving an operation delay caused by a liquid refrigerant at the initial operation.

Means for solving the problems

In order to achieve the above object, the present invention provides a swash plate type compressor including: a housing having a bore, a suction chamber, a discharge chamber, and a crank chamber; a rotating shaft rotatably mounted to the housing; a swash plate rotating together with the rotary shaft; pistons that are linked with the swash plate, reciprocate inside the bores, and form compression chambers with the bores; a first discharge passage that guides the refrigerant in the crank chamber to the suction chamber; and a second discharge passage that branches off from the first discharge passage and guides the refrigerant in the crank chamber to the suction chamber.

The first discharge passage may include: the first discharge passage upstream portion communicating with the crank chamber, the first discharge passage downstream portion communicating with the suction chamber, and the chamber between the first discharge passage upstream portion and the first discharge passage downstream portion, and the second discharge passage may include a second discharge passage upstream portion communicating with the chamber and a second discharge passage downstream portion communicating with the suction chamber.

The second discharge passage may be located radially outward of the first discharge passage and formed on one side in a gravitational direction with reference to the first discharge passage.

A first orifice for reducing a pressure of refrigerant passing through the first discharge passage may be formed at the first discharge passage, and a second orifice for reducing a pressure of refrigerant passing through the second discharge passage may be formed at the second discharge passage.

The first orifice may be formed coaxially with the rotation shaft, and the second orifice may be formed at a position spaced apart from the first orifice in a rotation radial direction of the rotation shaft.

The second orifice may be formed at one side in a gravity direction with reference to the first orifice.

The housing may include: a cylinder block having the bore formed therein; a front housing coupled to one side of the cylinder block and having the crank chamber formed therein; and a rear housing coupled to the other side of the cylinder block, the rear housing having the suction chamber and the discharge chamber formed therein, a valve mechanism interposed between the cylinder block and the rear housing, the valve mechanism communicating and shielding the suction chamber and the discharge chamber with the compression chamber, and the first orifice and the second orifice being formed in the valve mechanism.

The rear housing may include a strut that extends from an inner wall surface of the rear housing and supports the valve mechanism, and a communication path that communicates the second port and the suction chamber may be formed at the strut.

The communication path may be formed as a slit extending from a central portion of the front end surface of the pillar to an outer peripheral portion of the front end surface of the pillar.

The communication path may be formed as an inclined hole penetrating the pillar from a front end surface of the pillar to an outer peripheral surface of the pillar.

The pillars may be formed in at least one, the communication path may be formed at each pillar, and the second discharge passage and the second orifice may be formed corresponding to each communication path.

The cross-sectional flow area of the first orifice may be comprised in 1.54mm²Above and 4.52mm²In the following range, the sum of the flow cross-sectional areas of the at least one second orifice may be less than 125% of the flow cross-sectional area of the first orifice.

In addition, the present invention provides a swash plate type compressor including: a housing having a bore, a suction chamber, a discharge chamber, and a crank chamber; a rotating shaft rotatably mounted to the housing; a swash plate rotating together with the rotary shaft; pistons that are linked with the swash plate, reciprocate inside the bores, and form compression chambers with the bores; a first discharge passage that guides the refrigerant in the crank chamber to the suction chamber; and a second discharge passage bypassing the first discharge passage and guiding the refrigerant in the crank chamber to the suction chamber.

The first discharge passage may include a first discharge passage upstream portion communicating with the crank chamber, a first discharge passage downstream portion communicating with the suction chamber, and a chamber between the first discharge passage upstream portion and the first discharge passage downstream portion, and the second discharge passage may include a second discharge passage upstream portion communicating with the crank chamber and a second discharge passage downstream portion communicating with the suction chamber.

Effects of the invention

The swash plate type compressor according to the present invention includes: a housing having a bore, a suction chamber, a discharge chamber, and a crank chamber; a rotating shaft rotatably mounted to the housing; a swash plate rotating together with the rotary shaft; pistons that are linked with the swash plate, reciprocate inside the bores, and form compression chambers with the bores; a first discharge passage that guides the refrigerant in the crank chamber to the suction chamber; and a second discharge passage that branches off from the first discharge passage or bypasses the first discharge passage and guides the refrigerant in the crank chamber to the suction chamber. Therefore, the operation delay caused by the liquid refrigerant during the initial operation can be improved.

Drawings

Fig. 1 is a sectional view showing a conventional swash plate type compressor.

Fig. 2 is a sectional view illustrating a swash plate type compressor according to an embodiment of the present invention.

Fig. 3 is an enlarged view of a portion a of fig. 2.

Fig. 4 is a perspective view of fig. 3.

Fig. 5 is a perspective view showing the communication path of fig. 4.

Fig. 6 is a diagram showing operation delay characteristics of the swash plate compressor of fig. 2.

Fig. 7 is a diagram showing control characteristics of the swash plate compressor of fig. 2.

Fig. 8 is a sectional view illustrating a swash plate type compressor according to another embodiment of the present invention.

Fig. 9 is an enlarged view of a portion B of fig. 9.

Fig. 10 is a perspective view of fig. 9.

Fig. 11 is a perspective view showing the communication path of fig. 10.

Detailed Description

Hereinafter, a swash plate type compressor according to the present invention will be described in detail with reference to the accompanying drawings.

Fig. 2 is a sectional view showing a swash plate type compressor according to an embodiment of the present invention, fig. 3 is an enlarged view of a portion a of fig. 2, fig. 4 is a perspective view of fig. 3, fig. 5 is a perspective view showing a communication path of fig. 4, fig. 6 is a view showing an operation delay characteristic of the swash plate compressor of fig. 2, and fig. 7 is a view showing a control characteristic of the swash plate compressor of fig. 2.

Referring to fig. 2 to 7, a swash plate type compressor according to an embodiment of the present invention may include: a housing 100; and a compression mechanism provided inside the casing 100 and compressing the refrigerant.

The above-mentioned housing 100 may include: a cylinder block 110 accommodating a compression mechanism; a front housing 120 coupled to a front portion of the cylinder block 110; and a rear housing 130 coupled to a rear portion of the cylinder block 110.

The cylinder block 110 may have: a shaft hole 112 into which a rotary shaft 200 described later is inserted; and a chamber 114 communicating with the shaft hole 112. A hole 116 may be formed on the outer peripheral side of the cylinder block 110, and the hole 116 may be inserted with a piston 400 described later to form a compression chamber S2 together with the piston 400 described later. An inflow passage (not shown) described later, a first discharge passage 800 described later, and a second discharge passage 900 described later may be formed between the shaft hole 112 and the hole 116.

The shaft hole 112 and the chamber 114 may be formed in a circular pillar shape penetrating the cylinder block 110 in the axial direction of the cylinder block 110.

The hole 116 may be formed in a circular pillar shape penetrating the cylinder block 110 in the axial direction of the cylinder block 110 at a portion spaced outward from the shaft hole 112 in the radial direction of the cylinder block 110.

The number of the holes 116 may be n such that the number of the compression chambers S2 is n, and the n holes 116 may be arranged in the circumferential direction of the cylinder block 110 around the shaft hole 112.

The front housing 120 may be fastened to the cylinder block 110 from the front, and form a crank chamber S4 together with the cylinder block 110.

The crank chamber S4 can accommodate a swash plate 300, which will be described later.

The rear housing 130 may be fastened to the cylinder block 110 at an opposite side of the front housing 120 with respect to the cylinder block 110.

In addition, the rear case 130 may include: a suction chamber S1 for receiving the refrigerant flowing into the compression chamber S2; and a discharge chamber S3 for accommodating the refrigerant discharged from the compression chamber S2.

The suction chamber S1 may communicate with a refrigerant suction pipe (not shown) that guides a refrigerant to be compressed into the casing 100.

The discharge chamber S3 may communicate with a refrigerant discharge tube (not shown) that guides the compressed refrigerant to the outside of the casing 100.

The rear housing 130 may further include a strut 132, and the strut 132 may extend from an inner wall surface of the rear housing 130 to support a valve mechanism 500, which will be described later, to prevent the rear housing 130 from being deformed.

The strut 132 may include a communication path 920 for communicating a second orifice 910, which will be described later, with the suction chamber S1, to simplify the structure and reduce the cost.

The compression mechanism may be configured to suck a refrigerant from the suction chamber S1 into the compression chamber S2, compress the sucked refrigerant in the suction chamber S2, and discharge the compressed refrigerant from the compression chamber S2 to the discharge chamber S3.

Specifically, the compression mechanism may include: a rotary shaft 200 rotatably mounted to the housing 100 and rotated by receiving a rotational force from a driving source (e.g., an engine of a vehicle) (not shown); a swash plate 300 which rotates inside the crank chamber S4 in conjunction with the crank chamber S4; and a piston 400 reciprocating inside the bore 116 in conjunction with the swash plate 300.

The rotation shaft 200 may be formed in a circular pillar shape extending in one direction.

In addition, one end of the rotation shaft 200 may be inserted into the shaft hole 112 to be rotatably supported, and the other end may penetrate the front housing 120 and protrude to the outside of the housing 100 and be connected to the driving source (not shown).

The swash plate 300 may be formed in a disc shape and inclinedly fastened to the rotary shaft 200 in the crank chamber S4. Here, the swash plate 300 is fastened to the rotary shaft 200 in such a manner that the inclination angle of the swash plate 300 is variable, which will be described later.

The piston 400 may include: one end inserted into the hole 116; and the other end extending from the one end to the opposite side of the hole 116 and connected to the swash plate 300 in the crank chamber S4.

In addition, the piston 400 may have n number to correspond to the hole 116.

Further, the swash plate type compressor according to the present embodiment may further include a valve mechanism 500 for communicating and shielding the suction chamber S1 and the discharge chamber S3 with the compression chamber S2, and a first orifice 810 and a second orifice 910, which will be described later, may be formed in the valve mechanism 500.

In addition, the swash plate type compressor according to the present embodiment may further include a tilt adjusting mechanism for adjusting a tilt angle of the swash plate 300 with respect to the rotary shaft 200.

The tilt adjusting mechanism may include: a rotor 600 fastened to the rotary shaft 200 to rotate together with the rotary shaft 200 in such a manner that the swash plate 300 is fastened to the rotary shaft 200 and an inclination angle of the swash plate 300 is variably fastened; and a slide pin 700 connecting the swash plate 300 and the rotor 600.

Further, the inclination adjusting mechanism may include an inflow passage (not shown) guiding the refrigerant in the discharge chamber S3 to the crank chamber S4 to adjust the pressure in the crank chamber S4 to adjust the inclination angle of the swash plate 300, a first discharge passage 800 guiding the refrigerant in the crank chamber S4 to the suction chamber S1, and a second discharge passage 900 branching from the first discharge passage 800 guiding the refrigerant in the crank chamber S4 to the suction chamber S1.

The inflow passage (not shown) may extend from the discharge chamber S3 to the crank chamber S4 through the valve mechanism 500 and the cylinder block 110.

In addition, a pressure regulating valve (not shown) for controlling the opening amount of the inflow channel (not shown) may be formed at the inflow channel (not shown).

The above pressure regulating valve (not shown) may be formed by a so-called mechanical valve (MCV) or an electronic valve (ECV).

The first discharge passage 800 may penetrate one side of the cylinder block 110, penetrate one side of the valve mechanism 500 through the chamber 114, and extend from the crank chamber S4 to the suction chamber S1. That is, the first discharge passage 800 may include a first discharge passage upstream portion 800a communicating with the crank chamber S4, a first discharge passage downstream portion 800b communicating with the suction chamber S1, and a chamber 114 between the first discharge passage upstream portion 800a and the first discharge passage downstream portion 800 b.

In addition, a first orifice 810 for decompressing the refrigerant passing through the first discharge passage 800 may be formed in the first discharge passage 800 to prevent an increase in pressure in the suction chamber S1.

The first orifice 810 may be formed at the downstream portion 800b of the first discharge passage, and particularly, may be formed in the valve mechanism 500 for manufacturing convenience.

The first port 810 may be formed coaxially with the rotary shaft 200 such that the refrigerant discharged from the first port 810 to the suction chamber S1 is uniformly distributed to the n compression chambers S2. That is, the first orifice 810 may be formed at a center side of the valve mechanism 500.

The second discharge passage 900 may extend from the chamber 114 to the suction chamber S1 through the other side of the cylinder block 110 and the other side of the valve mechanism 500. That is, the second discharge passage 900 may include a second discharge passage upstream portion 900a communicating with the chamber and a second discharge passage downstream portion 900b communicating with the suction chamber S1.

In addition, a second orifice 910 for decompressing the refrigerant passing through the second discharge passage 900 is formed in the second discharge passage 900 to prevent an increase in pressure in the suction chamber S1.

The second orifice 910 may be formed in the downstream portion 900b of the second discharge passage, and particularly, may be formed in the valve mechanism 500 for ease of manufacturing.

The second orifice 910 may be formed at a position spaced apart from the first orifice 810 in the rotation radial direction of the rotary shaft 200, and may be preferably formed at one side in the gravity direction with respect to the first orifice 810, as will be described later, so that the liquid refrigerant accumulated in the lower portion of the crank chamber S4 is rapidly discharged into the suction chamber S1.

Here, it is preferable that the second discharge passage 900 is also formed at one side in the gravity direction with respect to the first discharge passage 800 so that the liquid refrigerant in the crank chamber S4 can be rapidly discharged into the suction chamber S1.

Hereinafter, the effect of the swash plate compressor according to the present embodiment will be described.

That is, when power is transmitted from the driving source (not shown) to the rotary shaft 200, the rotary shaft 200 and the swash plate 300 may be rotated together.

The piston 400 may convert the rotational motion of the swash plate 300 into a linear motion to reciprocate inside the bore 116.

When the piston 400 moves from the top dead center to the bottom dead center, the compression chamber S2 communicates with the suction chamber S1 through the valve mechanism 500 and shields the discharge chamber S3, so that the refrigerant in the suction chamber S1 can be sucked into the compression chamber S2.

When the piston 400 moves from the bottom dead center to the top dead center, the compression chamber S2 is shielded from the suction chamber S1 and the discharge chamber S3 by the valve mechanism 500, and the refrigerant in the compression chamber S2 can be compressed.

When the piston 400 reaches the top dead center, the compression chamber S2 is shielded from the suction chamber S1 by the valve mechanism 500 and communicates with the discharge chamber S3, and the refrigerant compressed in the compression chamber S2 can be discharged into the discharge chamber S3.

Here, in the swash plate type compressor according to the present embodiment, it is possible to adjust the pressure of the crank chamber S4 by adjusting the amount of refrigerant flowing from the discharge chamber S3 into the inflow passage (not shown) by a pressure adjusting valve (not shown) according to a required refrigerant discharge amount, and adjust the pressure of the crank chamber S4 applied to the piston 400, thereby adjusting the stroke of the piston 400, and adjusting the inclination angle of the swash plate 300, and adjusting the refrigerant discharge amount.

That is, when the refrigerant discharge amount needs to be decreased, the amount of refrigerant flowing from the discharge chamber S3 into the inflow channel (not shown) is increased by the pressure regulating valve (not shown), and the amount of refrigerant flowing into the crank chamber S4 through the inflow channel (not shown) is increased, so that the pressure in the crank chamber S4 can be increased. Here, the refrigerant in the crank chamber S4 is discharged into the suction chamber S1 through the first discharge passage 800 and the second discharge passage 900, but the amount of refrigerant flowing from the discharge chamber S3 into the suction chamber S1 through the inflow passage (not shown) is greater than the amount of refrigerant discharged from the crank chamber S4 into the suction chamber S1 through the first discharge passage 800 and the second discharge passage 900, and thus the pressure of the crank chamber S4 increases. Accordingly, the pressure applied to the crank chamber S4 of the piston 400 is increased, the stroke of the piston 400 is decreased, the inclination angle of the swash plate 300 is decreased, and the discharge amount of refrigerant is decreased.

On the other hand, when the required refrigerant discharge amount needs to be increased, the amount of refrigerant flowing from the discharge chamber S3 into the inflow passage (not shown) is reduced by a pressure regulating valve (not shown), and the amount of refrigerant flowing into the crank chamber S4 through the inflow passage is reduced, so that the pressure in the crank chamber S4 can be reduced. Here, even if the refrigerant in the discharge chamber S3 flows into the crank chamber S4 through the inflow passage (not shown), the pressure of the crank chamber S4 can be reduced because the amount of refrigerant discharged from the crank chamber S4 to the suction chamber S1 through the first discharge passage 800 and the second discharge passage 900 is greater than the amount of refrigerant flowing from the discharge chamber S3 into the crank chamber S4 through the inflow passage (not shown). Accordingly, the pressure of the crank chamber S4 applied to the piston 400 is reduced, the stroke of the piston 400 is increased, the inclination angle of the swash plate 300 is increased, and the refrigerant discharge amount is increased.

In addition, the swash plate type compressor according to the present embodiment includes the first discharge passage 800 having the first orifice 810 and the second discharge passage 900 having the second orifice 910, thereby preventing an evaporator connected to the swash plate type compressor from freezing while avoiding an operation delay at the time of initial operation.

Specifically, in the present embodiment, since the above-described first orifice 810 and the above-described second orifice 910 are included, the flow cross-sectional area of the entire orifice can be increased. Therefore, during the initial operation, the liquid refrigerant in the crank chamber S4 is smooth and smoothThe air is quickly discharged into the suction chamber S1, and as shown in fig. 6, the operation delay can be improved. That is, in fig. 6, the first sample corresponds to the prior swash plate type compressor having a flow cross-sectional area of 2.01mm²The second to fifth samples as swash plate compressors having a flow cross-sectional area of 2.01mm²And a first orifice 810 and a flow cross-sectional area of 0.54mm²、1.14mm²、1.8mm²And 2.52mm²The swash plate type compressor of the second orifice 910, corresponding to the swash plate type compressor of the present embodiment, can be seen that the operation delay time of the first sample takes about 43 seconds, and the operation delay time of the second to fifth samples takes about 20 to 39 seconds.

On the other hand, when only improvement of the operation delay is considered during the initial operation, a method of forming only the first discharge passage 800 and the first orifice 810 without forming the second discharge passage 900 and the second orifice 910 and increasing the flow cross-sectional area of the first orifice 810 may also be considered. That is, a method of increasing the flow cross-sectional area of the orifice in a conventional swash plate compressor may be considered. Even in this case, the operation delay time can be improved. That is, in fig. 6, the sixth sample is taken as a swash plate type compressor having one orifice equal to the flow cross-sectional area (3.81 mm) of the total orifice of the fourth sample²) In contrast, in the conventional swash plate compressor, the operation delay time of the sixth sample is about 24 seconds.

However, in this case (in the case of the sixth sample), as shown in fig. 7, the control characteristic of the swash plate compressor is significantly changed, and the discharge amount of the refrigerant is significantly different from the previously expected value, thereby possibly causing the evaporator to freeze. That is, the maximum capacity operation region of the compressor may be increased, and a compressor cycle (Cycling) may occur.

On the other hand, when the above-described second discharge passage 900 and the above-described second orifice 910 are additionally provided as in the present embodiment (the case of the second to fifth samples), the flow obstruction through the above-described second discharge passage 900 and the above-described second orifice 910, as shown in fig. 7, the control characteristic variation is small, the difference of the discharge amount of the refrigerant from the previous expected value is small, and the occurrence of icing in the evaporator is prevented. That is, an increase in the operating region of the maximum capacity of the compressor is suppressed, and the occurrence of compressor cycling can be reduced.

Therefore, not only the improvement of the operation delay during the initial operation but also the prevention of the evaporator freezing should be considered not to simply increase the flow cross-sectional area of the orifice like the sixth sample and the first sample, but preferably, the second discharge passage 900 having the second orifice 910 is formed separately from the first discharge passage 800 having the first orifice 810 like the present embodiment (the second sample to the fifth sample).

Also, in order to maximally improve the operation delay during the initial operation within a range in which the evaporator is prevented from freezing, the flow cross-sectional area of the first orifice 810 and the flow cross-sectional area of the second orifice 910 are preferably formed within predetermined ranges. That is, it is preferable that the flow cross-sectional area of the first orifice 810 is formed to be 1.54mm²Above and 4.52mm²In the range below, the flow cross-sectional area of the second orifice 910 is 125% or less of the flow cross-sectional area of the first orifice 810.

Here, when the flow cross-sectional area of the first orifice 810 is less than 1.54mm²In this case, there is a problem that the discharge of the liquid refrigerant is delayed and the operation is delayed, and the flow cross-sectional area of the first orifice 810 is larger than 4.52mm²Or, when the flow cross-sectional area of the second orifice 910 exceeds 125% of the flow cross-sectional area of the first orifice 810, there is a problem in that the operation region of the maximum capacity of the compressor is increased and the compressor cycle is increased.

On the other hand, in the present embodiment, the second discharge passage 900, the second orifice 910, and the communication path 920 are respectively formed in one, but are not limited thereto. That is, for example, the above-mentioned strut 132 is formed into at least one, the above-mentioned communication path 920 is formed in each strut 132, and the above-mentioned second discharge passage 900 and the above-mentioned second orifice 910 may be formed to correspond to each communication path 920. In this kind ofIn this case, the operation delay during the initial operation can be improved while preventing the evaporator from freezing more effectively. Here, it is preferable that the flow cross-sectional area of the first orifice 810 is formed to be included in 1.54mm²To 4.52mm²And the sum of the flow cross-sectional areas of the at least one second orifice 910 is comprised below 125% of the flow cross-sectional area of the first orifice 810.

On the other hand, in the present embodiment, the second discharge passage 900 branches from the first discharge passage 800, but as shown in fig. 8 to 11, the second discharge passage 900 may bypass the first discharge passage 800 separately from the first discharge passage 800 to guide the refrigerant in the crank chamber S4 to the suction chamber S1. That is, the second discharge passage 900 includes a second discharge passage upstream portion 900a communicating with the crank chamber S4 and a second discharge passage downstream portion 900b communicating with the suction chamber S1.

On the other hand, in the case of the present embodiment, the communication path 920 is formed as a groove extending from the center of the distal end surface of the support column 132 to the outer periphery of the distal end surface of the support column 132, for ease of manufacturing. As shown in fig. 8 to 11, the communication path 920 may be formed as an inclined hole penetrating the support 132 from the distal end surface of the support 132 to the outer peripheral surface of the support 132.

Claims

1. A swash plate type compressor comprising:

a housing having a bore, a suction chamber, a discharge chamber, and a crank chamber;

a rotating shaft rotatably mounted to the housing;

a swash plate rotating together with the rotary shaft;

pistons that are linked with the swash plate, reciprocate inside the bores, and form compression chambers with the bores;

a first discharge passage that guides the refrigerant in the crank chamber to the suction chamber; and

a second discharge passage that branches off from the first discharge passage and guides the refrigerant in the crank chamber to the suction chamber.

2. The swash plate type compressor according to claim 1,

the second discharge passage is located radially outward of the first discharge passage, and is formed on one side in the direction of gravity with reference to the first discharge passage.

3. The swash plate type compressor according to claim 1,

the first discharge passage includes: a first discharge passage upstream portion communicating with the crank chamber, a first discharge passage downstream portion communicating with the suction chamber, and a chamber between the first discharge passage upstream portion and the first discharge passage downstream portion,

the second discharge passage includes a second discharge passage upstream portion communicating with the chamber and a second discharge passage downstream portion communicating with the suction chamber.

4. The swash plate type compressor according to claim 1,

a first orifice for reducing a pressure of refrigerant passing through the first discharge passage is formed at the first discharge passage,

a second orifice for reducing the pressure of the refrigerant passing through the second discharge passage is formed at the second discharge passage.

5. The swash plate type compressor according to claim 4,

the first orifice is formed coaxially with the rotation shaft,

the second orifice is formed at a position spaced from the first orifice in a rotational radial direction of the rotary shaft.

6. The swash plate type compressor according to claim 5,

the second orifice is formed on one side in the direction of gravity with respect to the first orifice.

7. The swash plate type compressor according to claim 4,

the housing includes:

a cylinder block having the bore formed therein;

a front housing coupled to one side of the cylinder block and having the crank chamber formed therein; and

a rear housing coupled to the other side of the cylinder block and having the suction chamber and the discharge chamber formed therein,

a valve mechanism interposed between the cylinder block and the rear housing, the valve mechanism for communicating and shielding the suction chamber and the discharge chamber with the compression chamber,

the first and second orifices are formed in the valve mechanism.

8. The swash plate type compressor according to claim 7,

the rear housing includes a stay extending from an inner wall surface of the rear housing and supporting the valve mechanism,

a communication path that communicates the second orifice and the suction chamber is formed at the strut.

9. The swash plate type compressor according to claim 8,

the communication path is formed as a slit extending from a central portion of the front end surface of the pillar to an outer peripheral portion of the front end surface of the pillar.

10. The swash plate type compressor according to claim 8,

the communication path is formed as an inclined hole penetrating the pillar from a front end surface of the pillar to an outer peripheral surface of the pillar.

11. The swash plate type compressor according to claim 8,

the support post is formed in at least one shape,

the communication path is formed at each of the pillars,

the second discharge passage and the second orifice are formed to correspond to each communication path.

12. The swash plate compressor according to claim 11, wherein,

the cross-sectional flow area of the first orifice is comprised between 1.54mm²Above and 4.52mm²In the following range, the content of the polymer,

the sum of the flow cross-sectional areas of the at least one second orifice is less than 125% of the flow cross-sectional area of the first orifice.

13. A swash plate type compressor comprising:

a rotating shaft rotatably mounted to the housing;

a swash plate rotating together with the rotary shaft;

a second discharge passage bypassing the first discharge passage and guiding the refrigerant in the crank chamber to the suction chamber.

14. The swash plate compressor according to claim 13, wherein,

15. The swash plate compressor according to claim 13, wherein,

the first discharge passage includes a first discharge passage upstream portion communicating with the crank chamber, a first discharge passage downstream portion communicating with the suction chamber, and a chamber between the first discharge passage upstream portion and the first discharge passage downstream portion,

the second discharge passage includes a second discharge passage upstream portion communicating with the crank chamber and a second discharge passage downstream portion communicating with the suction chamber.