KR20110136212A - Compressor - Google Patents

Abstract

PURPOSE: A compressor is provided to improve the refrigerant compression efficiency of a compressor by simultaneously reducing the dead volume space in compressing the refrigerant and preventing the increasing of discharging resistance. CONSTITUTION: A compressor comprises a cylinder block, a front head, a rear head, a valve plate, an outlet valve and a piston(30). The piston has a piston protrusion(31). The piston protrusion comprises a base(31a) and a protrusion(31b). The base is parallelly projected from the piston in the movement direction of the piston. The cross section of the base vertical to the movement direction of the piston grows distant from the piston has the diminishing diameter at a fixed slope. The protrusion is parallelly projected from the base in the movement direction of the piston. The discharge hole formed in the valve plate comprises a penetration portion and a taper portion. The penetration portion perpendicularly passes through the valve plate. The taper portion is formed in one end of the penetration portion to slope.

Description

Compressor

The present invention relates to a compressor, and more particularly, to a compressor that can significantly improve the compression efficiency by minimizing the dead space during refrigerant compression and preventing an increase in the refrigerant discharge resistance.

The compressor used in the air conditioning system of the automobile sucks the evaporated refrigerant from the evaporator and transfers it to the condenser by making it easy to liquefy at high temperature and high pressure.

Such a compressor includes a reciprocating type for compressing a refrigerant and a reciprocating type for performing compression while the piston and the like reciprocate, and a rotary type for performing compression while the scroll and the like rotate. The reciprocating type includes a crank type for transmitting a driving force of a driving source to a plurality of pistons using a crank, a swash plate type for transferring a rotating shaft provided with a swash plate, and a wobble plate type using a wobble plate. Rotary type includes vane rotary type using rotary rotary shaft and vane, and scroll type using rotary scroll and fixed scroll.

1 shows a configuration of a general swash plate compressor in cross section. As shown in the figure, the skeleton and appearance of the compressor 10 are formed by the front head 11, the front cylinder block 12 and the rear cylinder block 12 ′, and the rear head 13. They are arranged and combined in the order of the front head 11, the front cylinder block 12, the rear cylinder block 12 'and the rear head 13.

The front head 11 has a substantially cylindrical shape and has a discharge chamber 11a formed therein. The discharge chambers 11a are opened toward the front cylinder block 12, respectively. The discharge chamber 11a is formed over a substantially ring-shaped region. The discharge chamber 11a is formed to be selectively connected to each cylinder bore 12a of the front cylinder block 12 through a valve assembly 20 to be described below.

The front head 11 penetrates through the center of the shaft hole (O) is formed. The shaft hole (O) is installed through the rotating shaft 14 to be described below.

The front cylinder block 12 and the rear cylinder block 12 'are coupled to the front head 11 and the rear head 13, respectively. A plurality of cylindrical cylinder bores 12a are formed in the front cylinder block 12 and the rear cylinder block 12 'in the direction of forming the shaft support hole 15 with the shaft support hole 15 as the center. . Of course, the cylinder bore 12a is formed at a position corresponding to the front cylinder block 12 and the rear cylinder block 12 ', respectively. The cylinder bore 12a and the shaft support hole 15 are connected to each other through a suction passage 15 ', respectively. The suction passage 15 ′ allows the refrigerant delivered through the inside of the rotating shaft 14 to be transferred to the cylinder bores 12a, respectively.

Discharge passages (not shown) are formed in the front cylinder block 12 and the rear cylinder block 12 ′ so as to communicate with the discharge chambers 11a and 13a of the front head 11 and the rear head 13, respectively. The discharge passage serves as a passage for discharging the refrigerant compressed in the cylinder bore 12a to the outside.

Refrigerant flow between the front head 11 and the front cylinder block 12 and between the discharge head 11a or 13a and the cylinder bore 12a between the rear head 13 and the rear cylinder block 12 '. The valve assembly 20 for controlling the is provided. That is, the valve assembly 20 controls the refrigerant flow from the cylinder bore 12a to the discharge chamber 11a or 13a.

The valve assembly 20 is provided with a valve plate 21. The valve plate 21 is formed in a substantially disk shape, and the valve plate 21 is formed with a discharge hole 21 'at a position corresponding to each cylinder bore 12a.

A discharge valve 22 is provided on one surface of the valve plate 21 facing the front head 11 and one surface of the valve plate 21 facing the rear head 13. The discharge valve 22 is a material capable of elastic deformation and elastically deforms according to the internal pressure of the cylinder bore 12a to open and close the discharge hole 21 '.

A communication hole (not shown) is formed at a position corresponding to the discharge passage of the valve plate 21. The communication hole serves to connect with the discharge passage.

The front cylinder block 12 and the rear cylinder block 12 'is formed with a recessed portion formed on the surface coupled to each other to form a swash plate chamber (16). In the swash plate chamber 16, the swash plate 17 provided on the rotation shaft 14 is rotatably positioned.

A rotating shaft 14 is installed through the center of the front head 11, the front cylinder block 12 and the rear cylinder block 12 '. The flow passage 14 ′ through which the refrigerant flows is formed in the rotation shaft 14. The flow passage 14 ′ is elongated in the longitudinal direction of the rotation shaft 14 inside the rotation shaft 14. An inlet 14a and an outlet 14b are formed on the outer surface of the rotation shaft 14. The inlet 14a connects the swash plate chamber 16 and the flow passage 14 ', and the outlet 14b is the suction passage 15' of the front cylinder block 12 and the rear cylinder block 12 '. It is formed at a position that can be connected to). The position of the outlet 14b should be formed in accordance with the compression order of the refrigerant proceeding in each cylinder bore 12a.

The shaft seal 18 is inserted into one side of the rotating shaft 14 to be in close contact with the inner surface of the shaft through hole (O) of the front head (11). The shaft seal 18 serves to prevent the refrigerant from leaking between the rotating shaft 14 and the shaft through hole (O). The shaft seal 18 is formed of a rubber material capable of elastic deformation.

An approximately disk-shaped swash plate 17 is inclined with respect to the extending direction of the rotating shaft 14 on the rotating shaft 14. A plurality of shoes 19 surrounding the edge of the swash plate 17 is installed. The shoe 19 is configured to move along the edge of the swash plate 17.

On the other hand, the piston 30 is installed inside the cylinder bore 12a to enable a straight reciprocating motion. The piston 30 has a substantially cylindrical shape corresponding to the inside of the cylinder bore 12a, and both ends thereof are located in the cylinder bore 12a of the front cylinder block 12 and the rear cylinder block 12 ', respectively. That is, both ends of one piston 30 serve to compress the refrigerant in the cylinder bore 12a. The piston 30 is the middle portion thereof is coupled to the shoe 19, the linear reciprocating motion in accordance with the rotation of the swash plate 17.

Meanwhile, as the piston 30 reciprocates, a piston protrusion 31 formed to be selectively inserted into the discharge hole 21 ′ protrudes from the piston 30 on the close contact surface in close contact with the valve plate 21. Is formed. When the piston 30 reciprocates, the piston 30 is in contact with the valve plate 21 and cannot proceed any further, resulting in a cylindrical body formed by the discharge hole 21 ′. The piston protrusion 31 is formed to improve the compression performance of the compressor by reducing such a dead volume.

Meanwhile, the rear head 13 is mounted on one surface of the rear cylinder block 12 '. The discharge chamber 13a is formed in the rear head 13. The discharge chamber 13a is formed over a substantially ring-shaped area. The discharge chamber 13a is opened toward the rear cylinder block 12 ', respectively. The discharge chamber 13a is selectively connected to the cylinder bores 12a formed in the rear cylinder block 12 'through the valve plate 21.

Pulley 40 is rotatably installed on one side of the front head (11). The pulley 40 is formed in a substantially cylindrical shape. The pulley 40 is rotated by receiving the driving force of the engine through a belt (not shown).

The field coil 41 is built in the pulley 40. The field coil 41 generates suction magnetic flux when the power is applied to allow the disk 46 to be described below to closely adhere to the friction surface 40 ′ of the pulley 40.

Meanwhile, a hub 43 is installed at one end of the rotary shaft 14, and a damper 44 is provided at the hub 43. The damper 44 absorbs the shock generated during power transmission between the rotary shaft 14 and the pulley 40. The damper 44 is provided to move the disk 46 in a position facing the friction surface 40 ′ of the pulley 40.

The operation of the compressor having such a configuration will be described. When the driving force of the engine is transmitted to the pulley 40 through the belt, the pulley 40 is rotated. However, if power is not applied to the field coil 41, the disk 46 is not in close contact with the friction surface 40 'of the pulley 40, so that the rotation shaft 14 does not rotate.

In this state, when the necessity of operation of the air conditioning system occurs and the compressor needs to be driven, the control system of the user or the vehicle provides a signal for the operation of the air conditioning system. When the operation of the air conditioning system is started and the refrigerant needs to be compressed, the field coil 41 generates suction magnetic flux while power is applied to the field coil 41.

When power is applied to the field coil 41, the disk 46 is in close contact with the friction surface 40 ′ of the pulley 40 by the suction magnetic flux of the field coil 41. Accordingly, the rotational force of the pulley 40 is transmitted to the rotation shaft 14 through the disk 46, the damper 44, and the hub 43.

When the rotational force of the pulley 40 is transmitted to the rotation shaft 14 as described above, the rotation shaft 14 rotates to linearly reciprocate the piston to compress the refrigerant.

At this time, as the rotary shaft 14 rotates, the flow passage 14 'inside the rotary shaft 14 is connected to the cylinder bore 12a through the outlet 14b and the suction passage 15'. The connection between the flow passage 14 ′ and the cylinder bore 12a allows the refrigerant sucked into the swash plate chamber 16 to be transferred to the cylinder bore 12a. For reference, the refrigerant is sucked into the cylinder bore 12a when the piston 30 is located at the bottom dead center of the corresponding cylinder bore 12a. As such, when the refrigerant is delivered to the cylinder bore 12a, the piston 30 of the corresponding cylinder bore 12a moves in the direction of the valve plate 21, and compression of the refrigerant occurs.

As such, when the refrigerant is compressed in the cylinder bore 12a, the pressure inside the cylinder bore 12a becomes relatively high, and the refrigerant is discharged into the discharge chambers 11a and 13a. The refrigerant discharged into the discharge chambers 11a and 13a is transferred to a condenser (not shown) through an external discharge port.

The refrigerant delivered to the condenser through the discharge port is delivered to the compressor again through a condenser (not shown), an expansion valve (not shown), and an evaporator (not shown). In the compressor the refrigerant is compressed by repeating the process described above.

At this time, the piston protrusion 31 is formed to improve the compression performance of the compressor by reducing the dead volume as already described. However, the coolant discharge resistance is increased by narrowing the coolant discharge flow path from the cylinder bore 12a to the discharge chambers 11a and 13a by the formation of the piston protrusion 31 when the compressor 10 is driven as described above. Compressor performance improvement due to the reduction of the dead volume has been minimal.

Accordingly, in order to improve the performance of the compressor by reducing the dead volume during refrigerant compression by forming the piston protrusion 31, the shape of the piston protrusion 31 which can minimize the refrigerant discharge resistance during refrigerant discharge and the discharge hole for accommodating the same ( 21 ') it is important to design the shape precisely.

Accordingly, an object of the present invention is to solve the problems of the prior art as described above, to provide a compressor that improves the refrigerant compression efficiency of the compressor by reducing the dead volume during refrigerant compression in the compressor and at the same time prevent the increase in discharge resistance will be.

Another object of the present invention is to provide a compressor that improves the cooling performance of the compressor by improving the discharge flow path of the compressor of the compressor.

According to a feature of the present invention for achieving the above object, the present invention is a cylinder block having a plurality of cylinder bores formed therein, respectively coupled to the front and rear of the cylinder block, the cylinder bore and A front plate and a rear head having a discharge chamber communicating therewith, a valve plate having a discharge hole communicating with the cylinder bore and the discharge chamber, a discharge valve provided to be elastically deformable to selectively shield the discharge hole, and a straight line. In the compressor comprising a piston protrusion selectively inserted into the discharge hole in accordance with the reciprocating motion, and comprising a piston for compressing the refrigerant by linear reciprocating motion in the cylinder bore, the piston projection from the piston Protrudes parallel to the direction of movement of the piston, perpendicular to the direction of movement of the piston The more cross-section moves away from the piston base and is formed to have a diameter that decreases at a constant gradient; And a protruding portion protruding in parallel to the direction of movement of the piston from the base portion, wherein the discharge hole includes: a through portion vertically penetrating the valve plate; It is formed to be inclined at one end of the through portion, it is configured to include a tapered portion having a cross section narrowed toward the through portion.

In this case, the protrusion may be formed to have a diameter that decreases at a constant slope smaller than a slope at which the diameter of the cross section of the base portion decreases as the cross section perpendicular to the direction of movement of the piston moves away from the base portion.

In addition, the difference (G _h ) between the height of the tapered portion and the height of the protrusion may have a value of 0 or more and 0.15 mm or less.

Furthermore, the minimum discharge effective diameter of the discharge flow path formed when the piston protrusion is inserted into the discharge hole is the discharge effective diameter of the discharge flow path formed by the discharge valve and the valve plate when the discharge valve is elastically deformed to open the discharge hole. This can be done.

)는 1.5 이상 3 이하의 범위 내로 한정되며, 상기 밸브플레이트의 수직방향과 상기 테이터부의 경사면이 이루는 각과 상기 기저부의 경사면이 상기 피스톤의 운동방향과 이루는 각 사이의 차(

)는 -10 이상 10 이하의 범위 내로 한정될 수 있다. Here, the ratio (R _A ) of the cross-sectional area of the piston perpendicular to the direction of movement of the piston and the maximum cross-sectional area of the base portion is defined within the range of 0.4 or more and 0.5 or less, and the angle at which the inclined surface of the protrusion forms the direction of movement of the piston. And the ratio of the angle of the inclined surface of the base to the direction of movement of the piston (

) Is defined within the range of 1.5 or more and 3 or less, and the difference between the angle between the vertical direction of the valve plate and the inclined surface of the data part and the angle between the inclined surface of the base part and the movement direction of the piston (

) May be defined within the range of -10 or more and 10 or less.

According to the compressor according to the present invention, the following effects can be obtained.

That is, the compressor according to the present invention has the advantage that the refrigerant compression efficiency of the compressor is improved by reducing the dead volume during refrigerant compression in the compressor and preventing the discharge resistance from increasing.

In addition, the compressor according to the present invention has the advantage that the cooling performance of the compressor can be improved by improving the discharge flow path of the compressor.

1 is a cross-sectional view showing the configuration of a typical rotary suction (Rotary Suction) compressor.
Figure 2a is a perspective view showing the protrusion shape of the compressor piston according to the embodiment of the present invention.
FIG. 2B is a cross-sectional view showing the cross-sectional shape of the compressor piston shown in FIG. 2A; FIG.
Figure 3a is a perspective view showing the shape of the compressor valve plate according to a specific embodiment of the present invention.
3B is a cross-sectional view showing a cross-sectional shape of the discharge hole of the compressor valve plate shown in FIG. 3A.
4 is a graph showing a change in compressor performance according to a specific embodiment of the present invention.
5 is a partial cross-sectional view showing the insertion process of the piston protrusion of the compressor into the discharge hole according to a specific embodiment of the present invention.

Hereinafter, an embodiment of a compressor according to the present invention will be described in detail with reference to the accompanying drawings. In particular, hereinafter, the main part of the present invention will be described, and other components of the compressor are similar to those described in the background art, and thus the description thereof will be omitted below. The same or similar configuration as the compressor described in the background will be described using the same reference numerals.

Figure 2a is a perspective view showing the projection shape of the compressor piston according to an embodiment of the present invention, Figure 2b is a cross-sectional view showing a cross-sectional shape of the compressor piston shown in Figure 2a, Figure 3a is a specific embodiment of the present invention Fig. 3B is a sectional view showing the cross-sectional shape of the discharge hole of the compressor valve plate shown in Fig. 3A. 4 is a graph showing a change in compressor performance according to a specific embodiment of the present invention.

First, the piston protrusions 31 of the compressor 10 according to the embodiment of the present invention will be described in more detail with the protrusion shape of the compressor piston according to the embodiment of the present invention. Protrude in parallel in the reciprocating linear motion direction from 30). In addition, the piston protrusion 31 has a circular cross section perpendicular to the direction of movement of the piston 30.

를 이루는 기저부(31a)와 상기 피스톤(30)의 운동 방향과 각

을 이루는 돌출부(31b)로 구성된다. 즉, 상기 기저부(31a)와 상기 돌출부(31b)는 선단으로 향할수록 상기 피스톤(30)의 운동 방향에 수직인 원형의 단면의 직경이 점차 작아지도록 형성된다. 여기서 각

는 각

보다 큰 값을 갖는다. 또한 상기 피스톤돌기(31)는 상기 피스톤(30)으로부터 전체적으로 높이 H₁을 갖도록 형성되며, 상기 기저부(31a)는 높이 h₁을 갖는다. 따라서 상기 돌출부(31b)만의 높이는 (H₁-h₁)이 된다. The piston protrusion 31 is formed integrally with the piston 30, and is formed to be inclined in two stages, the movement direction and the angle of the piston 30

Movement direction and angle of the base portion 31a and the piston 30 forming a

Consists of a protrusion (31b) forming a. That is, the base portion 31a and the protrusion portion 31b are formed such that the diameter of the circular cross section perpendicular to the direction of movement of the piston 30 gradually decreases toward the tip. Where each

Is each

Has a greater value. In addition, the piston protrusion 31 is formed to have a height H ₁ as a whole from the piston 30, the base portion 31a has a height h ₁ . Therefore, the height of only the protrusion part 31b becomes (H ₁ -h ₁ ).

In addition, when the diameter of the piston 30 in the cross section perpendicular to the direction of movement of the piston 30 is D, the base portion 31a has a diameter that is constantly reduced from the maximum diameter d ₁ to the minimum diameter d ₂ , The protrusion 31b has a diameter that constantly decreases from the maximum diameter d ₂ to the minimum diameter d ₃ of its tip.

Meanwhile, as shown in FIGS. 3A and 3B, the discharge hole 21 ′ of the valve plate 21 selectively accommodates the piston protrusion 31 according to the forward and backward reciprocating motion of the piston 30. A through portion 21b penetrating the plate 21 vertically and a tapered portion 21a forming an inclined surface from the valve plate 21 to the through portion 21b.

를 이룸으로써 도면에 도시된 바와 같이 상기 관통부(21b)를 향할수록 일정하게 감소하는 직경을 갖는다. 반면 상기 관통부(21b)는 상기 밸브플레이트의 수직 방향과 평행한 면으로 이루어짐으로써 그 직경이 d₄로 일정하다. 여기서 상기 밸브플레이트의 높이를 H₂, 상기 관통부의 높이를 h₂로 한다. The inclined surface by the tapered portion 21a is perpendicular to the vertical direction of the valve plate.

As shown in the figure, as shown in the figure, the diameter decreases constantly toward the through part 21b. On the other hand, since the through part 21b is made of a surface parallel to the vertical direction of the valve plate, its diameter is constant as d ₄ . Here, the height of the valve plate is H ₂ , and the height of the through part is h ₂ .

In order to more specifically limit the shapes of the piston protrusion 31 and the discharge hole 21 'to reduce the dead volume during refrigerant compression and to prevent the discharge resistance from increasing, the following equations Define the argument by

는 상기 피스톤(30)의 압축 방향 단면적의 넓이

와 상기 피스톤돌기(31)의 최대 직경에 의한 상기 피스톤돌기(31)의 최대 단면적의 넓이

사이의 비율을 정의한 것이고, 수학식 2에 나타낸 인자

는 상기 기저부(31a)가 상기 피스톤(30)의 운동 방향과 이루는 경사각

와 상기 돌출부(31b)가 상기 피스톤(30)의 운동 방향과 이루는 경사각

사이의 비율을 하나의 독립된 인자로 정의한 것이다. Where the factor shown in equation (1)

Is the width of the cross-sectional area in the compression direction of the piston (30)

And the width of the largest cross-sectional area of the piston protrusion 31 by the maximum diameter of the piston protrusion 31.

The ratio between

Is the inclination angle of the base portion 31a and the direction of movement of the piston 30

And the inclination angle between the protrusion 31b and the movement direction of the piston 30

The ratio between is defined as an independent factor.

는 상기 밸브플레이트(21)의 상기 테이퍼부(21a)가 상기 밸브플레이트(31)의 수직 방향, 즉 상기 피스톤(30)의 운동방향과 이루는 각

과 상기 피스톤돌기(31)의 상기 기저부(31a)와 상기 피스톤(30)의 운동방향이 이루는 각

사이의 차를 하나의 인자로 정의한 것이다. And the factor shown in Equation 3 above.

Is an angle between the tapered portion 21a of the valve plate 21 and the vertical direction of the valve plate 31, that is, the movement direction of the piston 30.

And an angle formed between the base portion 31a of the piston protrusion 31 and the movement direction of the piston 30.

The difference between the two is defined as a factor.

All of these defined factors are ratios or differences between specific values, which makes them applicable to various types or sizes of compressor piston protrusions and discharge holes.

With respect to the factors defined as above, the embodiment of the present invention limits the range of the above factors that can maximize the performance of the compressor 10.

The graph shown in FIG. 4 shows the relationship between the values of the three factors defined above, the volumetric efficiency (%) and the compressor coefficient of efficiency (COP) of the compressor.

는 대략 0.41의 값 부분에서 최대 체적 효율과 최대 성능 계수를 나타낸다. 그리고

는 -10에서 10도가 넘지 않는 범위 내에서 선택되는 것이 유리하다.As you can see in the graph

Represents the maximum volumetric efficiency and the maximum coefficient of performance in the value portion of approximately 0.41. And

Is advantageously selected within the range of -10 to no more than 10 degrees.

는 대략 2.5를 넘어서는 부분에서 높은 효율을 보임을 확인할 수 있다.Also

It can be seen that the high efficiency is shown in the portion exceeding approximately 2.5.

Based on these results, the numerical range of each of the above factors is limited as follows.

≤ 0.50.4 ≤

≤ 0.5

≤ 31.5 ≤

≤ 3

≤ 10
-10 ≤

≤ 10

In addition, the following parameters can be further defined.

The factor G _h represented by Equation 4 may be defined as a height difference between the height of the tapered portion 21a of the valve plate 21 and the protrusion 31b of the piston protrusion 31. Such G _h is helpful for compressor performance when it is adjusted within the range of 0 to 0.15.

Further, even when the piston protrusions 31 are formed, the piston protrusions 31 are accommodated in the discharge holes 21 ′ in order to prevent an increase in the refrigerant discharge resistance when the compressor 10 compresses the refrigerant. The minimum discharge effective diameter in the step is the width of the discharge flow path formed between the valve plate 21 and the discharge valve 22 when the discharge valve 22 is fully opened (hereinafter referred to as discharge effective diameter D _ed ). It is preferable to become above.

Here, the step in which the piston protrusion 31 is accommodated as the discharge hole 21 ′ may be divided into three stages as shown in FIG. 5, and the minimum discharge effective diameter is the piston in each stage shown in FIG. The narrowest cross-sectional area of the refrigerant discharge flow path formed between the projection 31 and the discharge hole 21 'is defined as a numerical value.

First, step (a) shown on the left side of FIG. 5 illustrates a step in which the tip of the piston protrusion 31 starts to enter the tapered portion 21a of the discharge hole 21 '.

Accordingly, the step (a) the minimum discharge effective diameter (D _e1) in the following is calculated by the following equation.

The minimum discharge effective diameter (D _e1) at the step (a) as identified in the equation (5) becomes a value obtained by subtracting the minimum cross-sectional area of the projecting portion (31b) at the maximum cross-sectional area of the tapered portion (21a).

In addition, the minimum ejection effective diameter D _e2 in step (b) illustrated in FIG. 5 is calculated as follows.

As confirmed in Equation 6, in step (b), the D _e2 is the minimum diameter d of the protrusion part 31b of the piston protrusion 31 in the cross-sectional area of the through part 21b of the valve plate 21. It becomes the value which subtracted the minimum cross-sectional area by ₃ .

Furthermore, the discharge minimum effective diameter (D _e3) in the step (c) shown in Figure 5 are the following operations in the same way.

As confirmed in Equation (7), in the step (c), D _e3 is the maximum diameter d of the protrusion part 31b of the piston protrusion 31 in the cross-sectional area of the through part 21b of the valve plate 21. It becomes the value which subtracted the maximum cross-sectional area by ₂ .

In three stages in which the piston protrusion 31 is accommodated in the discharge hole 21 ′, values of the three minimum discharge effective diameters calculated as described above are formed between the valve plate 21 and the discharge valve 22. It is preferable to be more than the discharge effective diameter D _ed .

The scope of the present invention is not limited to the embodiments described above, but is defined by the claims, and various changes and modifications can be made by those skilled in the art within the scope of the claims. It is self evident.

10: Compressor 11: Fronthead
11a: discharge chamber 12: front cylinder block
12 ': rear cylinder block 12a: cylinder bore
13: rear head 14: axis of rotation
14a: entrance 14b: exit
15: shaft supporter 15 ': suction passage
16: Judge Room 17: Judge
18: Holiday 19: Shoe
20: valve assembly 21: valve plate
21 ': discharge hole 21a: tapered portion
21b: through part 22: discharge valve
30: piston 31: piston protrusion
31a: base 31b: protrusion
40 ': Friction surface 41: Field coil
43: hub 44: damper
46: disk

Claims (5)

Cylinder blocks 12 and 12 'having a plurality of cylinder bores 12a formed therein, and coupled to the front and rear of the cylinder blocks 12 and 12', respectively, and communicating with the cylinder bores 12a therein. The front head 11 and the rear head 13 in which the discharge chambers 11a and 13a are formed, and the discharge holes 21 'communicating the cylinder bore 12a and the discharge chambers 11a and 13a are formed. A valve plate 21, a discharge valve 22 provided to be elastically deformable to selectively shield the discharge hole 21 ', and a piston selectively inserted into the discharge hole 21' according to a linear reciprocating motion. In the compressor (31) which is integrally formed to protrude and includes a piston (30) for compressing a refrigerant by linearly reciprocating in the cylinder bore (12a),
The piston protrusion 31,
The piston 30 protrudes in parallel to the direction of movement of the piston 30, and the cross section perpendicular to the direction of movement of the piston 30 has a diameter that decreases with a constant slope as it moves away from the piston 30. A base portion 31a formed;
It is configured to include a projection (31b) protruding in parallel to the movement direction of the piston 30 from the base portion (31a),
The discharge hole 21 ′,
A through part 21b vertically penetrating the valve plate 21;
And a tapered portion (21a) formed to be inclined at one end of the through portion (21b) and having a cross section narrowing toward the through portion (21b). The method of claim 1,
The protrusion 31b,
As the cross section perpendicular to the direction of movement of the piston 30 moves away from the base portion 31a, the cross section of the piston 30 is formed to have a diameter that decreases with a constant slope smaller than the slope of which the diameter of the cross section of the base portion 31a decreases. Compressor. The method of claim 1,
And a difference (G _h ) between the height of the tapered portion (21a) and the height of the protrusion (31b) has a value between 0 and 0.15 mm. The method according to claim 2 or 3,
The minimum discharge effective diameters D _e1 , D _e2 , and D _e3 of the discharge flow paths formed when the piston protrusions 31 are inserted into the discharge holes 21 ′ are such that the discharge valve 22 is elastically deformed and the discharge is performed. And a discharge effective diameter (D _ed ) of the discharge flow path formed by the discharge valve (22) and the valve plate (21) when the ball (21 ') is opened. The method of claim 3,
The ratio R _{A of the} cross-sectional area of the piston 30 perpendicular to the direction of movement of the piston 30 and the maximum cross-sectional area of the base portion 31a is limited within the range of 0.4 or more and 0.5 or less,
The ratio of the angle at which the inclined surface of the protruding portion 31b is formed to the direction of movement of the piston 30 and the angle at which the inclined surface of the base portion 31a is formed at the movement direction of the piston 30 (

) Is limited to the range from 1.5 to 3,
The difference between the angle between the vertical direction of the valve plate 21 and the inclined surface of the data portion 21a and the angle between the inclined surface of the base portion 21a and the movement direction of the piston 30 (

) Is limited to within the range of -10 or more and 10 or less.

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