JP2000161220A - Reciprocating compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce noises by communicating a pressure introducing part of a resonance chamber with a delivery hole. SOLUTION: A pressure introducing part 601 opening in a delivery hole 34 is provided in a valve plate 6 unused part, and a resonance chamber 60 being a space part by applying a theory of a Helmholtz resonator is arranged. The resonance chamber 60 is composed of a through hole part 600, and in the upper/lower ends of the hole part 600, one is closed by a delivery valve 34, and the other is closed by a suction valve 32. The two valves are fixed by a fixing bolt 650. The delivery valve 34 is supported by retainer 36, and even if the delivery valve 34 is opened/closed, since the delivery valve exists in the root direction of the retainer 36, a space of the resonance chamber 60 is formed by being sandwiched with a valve plate 6. Similarly, the suction valve 32 is also fixed by the fixing bolt 650, a part is sandwiched by a cylinder block and the valve plate 6 to form a space of the closed resonance chamber 60. Noise can be reduced by easily using the valve plate by paying attention to a frequency of problematic specific noise.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating compressor, and more particularly, to a reciprocating compressor suitable for use in vehicle air conditioning, which is mainly a multi-cylinder reciprocating compressor having a single-headed piston. Type compressor.

[0002]

2. Description of the Related Art Conventionally, as this type of compressor, there are known a constant displacement compressor having a fixed swash plate and a so-called variable displacement compressor in which the inclination angle of a rotary swash plate is displaceable and the displacement is variable. And are used in air conditioners for vehicles.

As a variable displacement compressor, a compressor (compressor) for vehicle air conditioning for circulating a cooling gas as a refrigerant to an air conditioning system, for example, as shown in FIG. , A reciprocating compressor (hereinafter simply referred to as a compressor) 1 for obtaining the following is known. This compressor 1 is of a variable capacity type that makes the suction capacity of the cooling gas variable, and a plurality (for example, 7
One) piston.

[0004] As shown in FIG. 6, a compressor casing 2 as a housing serving as a pressure vessel is formed by assembling a front housing 3, a cylinder block 4, a cylinder head 5, a valve plate 6, and the like. It is formed.

[0005] In the compressor casing 2, a notch groove 4 a is formed in a joining surface on one end side of a cylinder block 4 connected to the front housing 3 in order to maintain the airtightness of the internal space.
Is provided, and an O-ring (not shown) as a sealing material is attached to the cutout groove 4a. Also,
In the compressor casing 2, the cylinder block 4 and the valve plate 6
A cylinder gasket and a head gasket are respectively attached as a sealing material at a joint portion between the cylinder head 5 and the valve plate 6. In FIG. 6, only the cylinder gasket 7 between the cylinder block 4 and the valve plate 6 is shown for convenience.

A drive shaft 8 rotatably housed in the compressor casing 2 and a plurality of pistons reciprocating in the cylinder block 4 by the rotation of the drive shaft 8 are provided.

Specifically, in the compressor casing 2, through holes 11 and 12 for supporting the drive shaft 8 are formed in the center of the front housing 3 and the center of the cylinder block 4, respectively. Each of these through-hole portions 11,
The drive shaft 8 is rotatably attached to the drive shaft 12 via bearings 13 and 14, a drive shaft support member 15, and the like.

[0008] Around the through hole 12 in the cylinder block 4, the cylinders 16 for accommodating the pistons are provided by the number of the pistons 10. Cylinder 16
Are formed in a direction in which the piston 10 reciprocates in parallel with the axial direction of the drive shaft 8, as shown in FIG. In the compressor casing 2, the space below the through hole 12 and the cylinder 16 (left side in the figure) is the crank chamber 1.
The drive shaft 8 rotates in the crank chamber 17, and accordingly, a swing plate 22 described below swings.

Here, the rotor 18 is connected to the drive shaft 8.
Are fixed by rotor rotation stopping pins 19, and a swash plate boss 21 is connected to the rotor 18. A swing plate 22 is attached to the swash plate boss 21, and the swing plate 22 is
Each of the pistons 10 is connected via a universal joint (universal joint) 3 to each other.

More specifically, the rotor 18 and the swash plate boss 21 have ears 24 and 25, respectively, and the engaging pin 24a provided on the ear 24 on the rotor 18 side is used as the swash plate boss 21. By movably engaging the long ear portion 25a formed with a predetermined size with the side ear portion 25, connection is achieved by a so-called hinge mechanism.

The rocking plate 22 includes a bearing 2
The swash plate boss 21 and the swash plate boss 21 are rotatably attached to the swash plate boss 21 through the swash plate boss 21. Thus, even if the swash plate boss 21 rotates, the swing plate 22 does not rotate with it.

On the other hand, the valve plate 6 is located inside the compressor casing 2 so as to be sandwiched between the cylinder block 4 and the cylinder head 5 by screwing. The valve plate 6 is provided with suction holes 31 for sucking the cooling gas into the cylinder 16 and discharge holes 35 for discharging the cooling gas in the cylinder 16 to the outside, the number of which is equal to the number of the pistons 10. Further, a spring-shaped suction valve (not shown) and a discharge valve 35 are attached to the valve plate 6 so as to close the suction hole 31 and the discharge hole 33.

Here, the suction valve is mounted on the main surface of the valve plate 6 facing the cylinder block 4, and is a valve receiving portion (recess) 3 which is a cutout groove formed in the cylinder block 4.
The amount of movement (lift amount) of the valve 3 is restricted by the contact of the distal end of the valve with the valve 3. On the other hand, the discharge valve 35 is mounted on the main surface of the valve plate 6 facing the cylinder head 5. A retainer 36 having the same planar shape as the discharge valve 35 and restricting the lift of the discharge valve 35 is attached to the upper side (right side in the figure) of the discharge valve 35.

The cylinder head 5 has a substantially bowl shape, and has a partition wall 41 formed therein. Cylinder head 5
The partition 41 separates the internal space into a suction chamber 42 and a discharge chamber 43. Here, the suction chamber 42 communicates with the suction hole 31 of the valve plate 6 and forms a flow path of the cooling gas to the plurality of cylinders 16 via the suction valve.

The discharge chamber 43 communicates with the discharge hole 34 of the valve plate 6 through the discharge valve 35, and discharges cooling gas from the plurality of cylinders 16 to the outside through the discharge valve 35. It becomes a flow path. Although not shown, the cylinder head 5 is provided with a suction port for supplying the cooling gas to the suction chamber 42 and a discharge port for sending the cooling gas from the discharge chamber 43 to the outside.

In the compressor 1 having such a configuration, the driving shaft 8 is driven by an external driving force such as an engine or a motor.
When the rotor rotates, the rotor 18 rotates integrally, and its rotational motion is transmitted to the swash plate boss 21 via the hinge mechanism described above, and the swash plate boss 21 rotates synchronously with the drive shaft 3 at a predetermined inclination angle.

The swinging plate 22 rotatably connected to the swash plate boss 21 has one end thereof on the guide member 2.
By reciprocating along 8, it swings at a predetermined inclination angle without rotating in the crank chamber 17. At this time, in the compressor 1, the plurality of pistons 10 reciprocate in the cylinder 16, and the pistons 10 that have reached the positions of the ears 24 of the rotating rotor 18 are sequentially pushed up so as to reach the top dead center. Become.

In the compressor 1, a cooling gas from a gas-liquid separator, an evaporator (evaporator) or the like (not shown) is supplied to a suction chamber 42 in the cylinder head 5, and when the piston 10 moves to the bottom dead center side, suction is performed. The valve opens and the cooling gas is drawn into the cylinder 16. When the piston 10 moves to the top dead center side, the cooling gas in the cylinder 16 is compressed, the discharge valve 35 is opened by the compressed cooling gas, and the cooling gas is discharged to the discharge chamber 13. And
The cooling gas is discharged to the outside from the discharge port of the cylinder head 5 and supplied to a radiator (not shown).

In such a compressor, the opening and closing operation of the suction valve is performed by lowering the piston 10 so that the gas pressure in the bore is lower than that of the suction chamber, and the force acting on the suction valve surface closing the suction hole. Exceeds the sum of the bending stress of the suction valve, the pressure in the bore and the viscous force of the oil between the valve and the valve plate,
The valve opens, and conversely, closes if it falls below.

However, in a fixed displacement compressor having a fixed swash plate or a variable displacement compressor having a rotary swash plate capable of tilting displacement, the cylinder 16 is moved by the upward movement of the piston 10 during the compression stroke. Due to friction with the wall, a minute vibration is generated, which pulsates the discharged refrigerant gas flow. As a result, vibration and noise occurred.

A rotary compressor in which a muffler chamber is provided outside the compressor on the discharge side to reduce these noises, and a Helmholtz type resonator is provided in a gas passage connecting the muffler chambers is disclosed in Japanese Patent Application Laid-Open No. H10-260,086. No. 7,247,974.

A rotary compressor in which a Helmholtz type resonator communicating with the compressor is provided at a bearing portion of the rotary compressor in order to reduce these noises is disclosed in Japanese Utility Model Application Laid-Open No. H10-410.
0092.

In addition, the suction valve has a problem of vibration and noise. As shown in FIG. 6, when the flow rate of the refrigerant gas is relatively small, for example, when the operation of the compressor is started or the heat load is small, the opening amount of the suction valve decreases.
Without coming into contact with the stopper, it floats in the refrigerant gas, causing self-excited vibration to cause suction pulsation, which causes vibration and noise.

As such a measure, for example, it has been proposed to improve the shape and structure of the valve receiving portion 33.

The valve receiving portion 33 is formed at the upper end of each cylinder 16 of the cylinder block 4 as shown in FIG. 6 (or FIGS. 2 and 3). Each valve receiving part 33
Is a cutout groove formed at a predetermined depth from a joint plane to be joined to the cylinder gasket 7, and has a substantially crescent-shaped plane. The valve receiving portion 33 is provided with the through-hole portion 12.
Are formed on the upper end side of each cylinder 16 on an extension of an imaginary line connecting the center of the circle formed by the circle and the center of the circle formed by the cylinder 16.

The suction valve 32 is mounted on the main surface of the valve plate 6 facing the cylinder block 4.
The amount of movement (lift) of the valve is limited by the tip of the valve abutting against a valve receiving portion (recess) 33 which is a notched groove formed in the cylinder block 4.

In such a valve receiving portion 33, it has been proposed to make the depth of the valve receiving portion 33 shallow or to make the valve receiving portion 33 oblique. It has also been proposed to dispose the suction valve 32 at a biased position.

[0028]

In these compressors, the upward movement of the piston 10 during the compression stroke of the compressor causes micro-vibration due to friction with the wall of the cylinder 16 and pulsates the flow of the discharged refrigerant gas. In order to eliminate the cause of vibration and noise,
As for the methods of increasing the volume of the cylinder head 3 or reducing the diameter of the discharge port 37 provided in the cylinder head 5, the former method requires the cylinder head 5 to be large, and, for example, increases the space for mounting the vehicle. . In the latter case,
The method of reducing the diameter of the discharge port 37 causes a pressure loss of the discharged refrigerant, and increases the temperature of the discharge gas whose discharge pressure increases,
Then, there is a problem that the oil is deteriorated and the performance is deteriorated.

In order to reduce these noises, a rotary compressor is provided with a muffler chamber outside the compressor on the discharge side, and a Helmholtz type resonator is provided in a gas passage connecting the muffler chambers. However, in this case, a space for separately providing a muffler chamber is required, and the gas passage is narrow and limited.

In order to reduce these noises, a rotary compressor provided with a Helmholtz type resonator communicating with the compressor at a bearing portion of the rotary compressor is disclosed in Japanese Utility Model Application Laid-Open No. 4-100.
No. 092, the compressor itself is also different in type and reduces noise in the compression chamber. It is also in a bearing adjacent to the compression chamber, and its use space is also limited. It is difficult.

In the conventional multi-cylinder compressor 1,
For example, when the operation of the compressor is started or when the heat load is small, the opening amount of the suction valve decreases, so that the suction valve does not come into contact with the stopper, but floats in the refrigerant gas, and is self-excited. In order to improve the point that causes vibration and causes suction pulsation and causes vibration and noise, to reduce the depth of the valve receiving portion 33,
At the time of suction, the flow passage area of the suction is substantially narrowed, thereby increasing the flow passage resistance. Therefore, there is a problem that the pressure loss increases and the compression performance decreases.

Also, due to the problem of noise in the suction valve 32, the method of making the valve receiving portion 33 oblique is to contact the shallow position of the valve receiving portion 33 at a low flow rate, and to twist the valve obliquely at a high flow rate. The contact makes it possible to secure a flow path. However, this method has a problem that pulsation due to torsional vibration occurs due to torsion caused by the valve at a high flow rate. In addition, any modification of the conventional method based on the shape, rigidity, etc. of other valves has caused some inconvenience and has not yet been solved.

The present invention has been proposed in view of such circumstances. In a fixed displacement compressor having these fixed swash plates or a variable displacement compressor having a rotating swash plate capable of tilting displacement, friction between the piston 10 and the wall of the cylinder 16 during the upward movement of the piston 10 in the compression stroke causes Reciprocating motion that can easily reduce these noises by focusing on the specific noise frequency that causes these vibrations and noises by generating pulsation in the discharged refrigerant gas flow due to micro vibrations It is an object to provide a type compressor.

Further, the present invention focuses on the frequency of specific noise caused by the generation of cooling gas sucked from the suction chamber into the suction hole of the valve plate due to the pulsation of the suction valve. It is an object of the present invention to provide a reciprocating compressor capable of reducing the pressure.

According to the present invention, not only the noise due to the pulsation on the discharge side but also the noise due to the pulsation of the suction valve can be reduced, and the structure of the compressor is simple and inexpensive without any reduction in the performance of the compressor. It is an object to provide a reciprocating compressor.

According to the present invention, the noise due to the pulsation can be reduced without requiring any special device or equipment, and without increasing the size of the compressor.
It is an object of the present invention to provide an inexpensive reciprocating compressor that can be reduced by providing a structure for noise reduction in the structure of an existing compressor.

[0037]

In order to solve the above-mentioned problems, the present invention focuses on the frequency of self-excited vibration of a valve body. Of course, the frequency of the self-excited vibration is not constant and varies depending on the flow rate of the refrigerant and the like. However, the frequency of the operation of the compressor, the number of cylinders, the natural frequency of the components of the air conditioner system, and the like. It has been found from experiments and the like that the frequency, which is a significant noise problem due to a complicated correlation, is limited. Therefore, if the frequency range of the frequency that causes this problem can be attenuated, noise can be reduced.

Therefore, in the present invention, the rotational driving force transmitted from the external drive source to the drive shaft is transmitted to the piston through the crank mechanism, and the cooling gas sucked from outside is sucked and compressed by the piston, and the air conditioning system In a reciprocating compressor that circulates through, a front housing in which the drive shaft is rotatably mounted, and a cylinder in which the piston is housed and connected to the front housing are provided as constituent members of a housing serving as a pressure vessel. A cylinder plate, a valve plate connected to the cylinder block, and a valve plate to which a suction valve for sucking cooling gas supplied from the outside into the cylinder by moving the piston to the bottom dead center side is attached; and Connected to the suction chamber for supplying a cooling gas supplied from the outside to the suction valve and the cooling gas compressed by the piston. A cylinder head or the like in which a discharge chamber for discharging to a portion is formed, wherein a resonance chamber comprising a space portion to which the damping action of the Helmholtz resonator is applied is provided on a valve plate, wherein a pressure introducing portion of the resonance chamber is provided. The present invention provides a reciprocating compressor in which is communicated with a discharge hole.

In the resonance chamber which is a space provided in the valve plate to which the damping action of the Helmholtz resonator is applied, the resonance chamber is provided in a portion closed by a discharge valve and a suction valve.

In the resonance chamber which is a space provided in the valve plate to which the damping action of the Helmholtz resonator is applied, the resonance chamber has a through hole, and the hole is closed by a discharge valve and a suction valve. It is provided in the portion provided.

In the resonance chamber, which is a space provided in the valve plate to which the damping action of the Helmholtz resonator is applied, other parts other than the resonance chamber provided in a part closed by a discharge valve and a suction valve are provided. Are provided.

In the resonance chamber, which is a space provided in the valve plate to which the damping action of the Helmholtz resonator is applied, a resonance chamber is provided on the discharge side where the pressure introduction section communicates, and the pressure introduction section is provided on the discharge side or the suction side. Another resonance chamber is provided for communication.

[0043]

Embodiments of the present invention will be described below with reference to the drawings based on embodiments. 1 or 2
The same reference numerals as those in FIG. 6 denote the same members, and a description thereof will be omitted as appropriate to avoid redundancy. The compressor 1 shown in FIG. 1 to which the present invention is applied is a reciprocating compressor that obtains a compression force by reciprocating pistons as in FIG. 6, and is a variable displacement type that makes the compression capacity of the cooling gas variable. belongs to.

In the compressor 1 to which the present invention is applied, specifically, the configuration of the valve plate 6 is different for noise reduction. The configuration of the compressor 1 will be described in detail.
As shown in the figure, the front housing 3, the cylinder block 4, the cylinder head 5, the valve plate 6, etc. are assembled.
Here, the front housing 3, the cylinder head 5, and the valve plate 6 are the same members as the front housing 3, the cylinder head 5, and the valve plate 6 of the conventional compressor.

As shown in FIG. 6, the compressor 1 has seven cylinders 16 around the through hole 12 of the cylinder block 4.
, And the valve plate 6, the cylinder gasket 7, the intake valve 32 and the discharge valve 35 made of a spring material, the retainer 36, and the like have shapes corresponding to the number of cylinders. That is, each of the suction valve 32, the discharge valve 35, and the retainer 36 is a plate-shaped member radially branched in seven directions from the center. The valve plate 6 is provided with seven suction holes 32 and seven discharge holes 34.

The distal end of each valve in the intake valve 32 closes each intake hole 32 of the valve plate 6, the distal end of each valve in the discharge valve 35 closes each discharge hole 34 of the valve plate 6, and the retainer 36. Are fixed by screws so as to be flush with the discharge valve 35. Thereby, each of the substantially oval holes (not shown) for the passage of the discharge gas formed in the suction valve 32 on the base end side of each valve communicates with each discharge hole 34 of the valve plate 6. .

The suction valve 32, the valve plate 6, the discharge valve 35, and the retainer 36 are stacked in this order and screwed. At this time, the distal end side of each valve in the intake valve 32 closes each intake hole 31 of the valve plate 6, the distal end side of each valve in the discharge valve 35 closes each discharge port 34 of the valve plate 6, and the retainer 36 discharges. The valve 35 is fixed by screwing so as to be flush with the plane. Thereby, a substantially oval hole 4 for discharging gas passing through the suction valve 32 at the base end side of each valve.
Each of the nozzles 8 communicates with each of the discharge holes 34 of the valve plate 6.

As shown in FIG. 2, a valve receiver 33 is formed at the upper end of each cylinder 16 of the cylinder block 4. Each of the valve receiving portions 33 is a cutout groove formed at a predetermined depth from a joint plane serving as a joint portion with the cylinder gasket 7, and has a substantially crescent-shaped plane. Each valve receiving portion 33 is formed at a position on the upper end side of each cylinder 16 on an extension of an imaginary line connecting the center of the circle formed by the through-hole portion 12 and the center of the circle formed by the cylinder 16.

By assembling these members using a plurality of screws, the tip of each valve in the suction valve 32 is arranged at the position of each valve receiving portion 33 of the cylinder block 4.

Therefore, in the present invention, as shown in FIG. 2A, which is an enlarged portion of the portion A in FIG. 1, the pressure introduction opening to the discharge hole 34 is formed in the unused portion of the valve plate 6. A resonance chamber 60, which is a space provided with a section 601 and to which the Helmholtz resonator theory is applied, is provided.

In the present embodiment, the resonance chamber 60 is formed of a through hole 600, and the upper and lower ends of the hole 600 are
One is closed by the discharge valve 34 and the other is closed by the suction valve 32, and the two valves are fixed by fixing bolts 650. The discharge valve 34 is supported by the retainer 36, and even if the discharge valve 34 is opened or closed,
, The resonance chamber 60 is sandwiched by the valve plate 6.
To form a space. Similarly, the suction valve 32 is also fixed by a fixing bolt 650, and this portion forms a closed space of the resonance chamber 60 sandwiched between the cylinder block 4 and the valve plate 6.

Further, in this embodiment, the resonance chamber 60 is formed from the through hole 600, but is not a through hole as shown in FIG. There may be. On the contrary, the resonance chamber 60 may be a concave part whose upper side is opened. In any case, since the resonance chamber 60 is provided in a region closed by the suction valve 32 and the discharge valve 35, a so-called lid material is required. And there is no convenience.

Accordingly, the resonance chamber 60 does not require any special closing member to close the through hole 600, and the existing valve plate 6, discharge valve 34, suction valve 32, retainer 36, cylinder It can be provided using the block 4 and the fixing bolt 650.

As a theoretical expression based on the Helmholtz resonator, in a resonator as shown in FIG. 7, the silencing volume R due to the Helmholtz resonator is generally given by Equation 1.

[0055]

(Equation 1)

As shown in this equation, the silencing volume has a maximum value at the resonance frequency, and the resonance frequency _fr is given by the following equation (2).

[0057]

(Equation 2)

In the case of G, the length of the pressure introducing portion is short when the hole has a circular conductivity and the diameter is d. For example, when d ≒ L, G = S / L = πd ² / from 4L = πd / 4 ≒ d, resonance frequency f _r is given by Equation 3.

[0059]

(Equation 3)

[0060] Therefore, in this case, it can be adjusted according to the frequency of the pulsating resonance frequency f _r by changing the volume V.

Thus, when the frequency of the noise generated from the pulsation of the discharge flow matches the natural frequency in the resonance chamber 60,
Therefore, the vibration frequency due to the self-excited vibration is measured in advance, and the natural frequency of the resonance chamber 60 is determined according to the vibration frequency. The volume of the resonance chamber 60 is
For example, about 0.03 to 0.5 cm ³ can be considered.

FIG. 3 shows another embodiment,
The resonance chamber 61 is also provided on the suction hole 31 side of the discharge hole 34. The pressure introducing section 602 communicates with the discharge hole 34. As shown in the plan view of the valve plate 6 shown in FIG.
Are communicated with the discharge hole 34 by the pressure introducing portion 602. The resonance chamber 61 may be provided independently without the previous resonance chamber 60, but in this case, the formation thereof requires some contrivance in terms of man-hours.

When the resonance chamber 61 is used as an internal space, a step is required for its formation. Therefore, as shown in FIG.
The upper 6a and the lower 6
If it is formed as b, one of them plays a role of a lid for closing the resonance chamber 61, so that the production of the resonance chamber 61 is further facilitated.

In this case, as shown in FIG. 3, the pressure introducing portion 601 and the pressure introducing portion 602 can be formed along the cutting line, and can be easily provided as grooves by cutting.

As described above, by forming the resonance chamber around the discharge hole 34, it is possible to reduce the noise caused by the pulsation of the discharge flow.

Further, as shown in FIG. 5, it is also possible to adopt a configuration in which not only the noise due to the pulsation on the discharge side but also the noise from the suction valve 32 is reduced. In (2) of FIG. 5, the resonance chamber is provided with resonance chambers 62 and 63 in which pressure introduction parts 602 and 603 communicate with the suction hole 31 in addition to the resonance chamber 60.

In this embodiment, the resonance chamber 62 is provided with the pressure introducing portion 602 opened to the suction hole 31 side in order to reduce noise caused by the pulsation of the suction valve. Or at a portion that can be arranged on either side of the suction hole 31, which can contribute to noise reduction of the entire compressor. As described above, the resonance chamber provided between the suction hole and the discharge hole is located at such a position that the pressure introducing portion can be disposed in both directions. As shown in FIG. 4, it can be seen that the resonance chamber 61 is disposed in the valve plate 6, and it can be seen that the pressure introduction part can be opened on either the suction side or the discharge side, and the resonance chamber 61 can be provided and applied. .

When manufacturing these resonance chambers, it goes without saying that a cutting configuration as shown in FIG. 3 can be similarly employed. In particular, the depth of the resonance chambers 62 and 63 is determined by (2) in FIG.
The upper part 6a to be cut horizontally can be formed as a single disk-shaped plate if the depths are matched.

In providing the outer resonance chamber in the compressor, it is obvious that those skilled in the art can make various modifications in applying the technical idea of the present invention.

In the above-described embodiment, an example of a compressor has been described. However, the present invention is not limited to this.
The present invention is also applicable to various similar compressors such as a single swash plate type.

[0071]

As described above in detail, according to the reciprocating compressor of the present invention, it has been proposed in view of the conventional situation, and is a constant displacement type compressor having these fixed swash plates. In a compressor or a variable displacement compressor equipped with a rotary swash plate capable of tilting displacement, micro-vibration occurs due to friction with the cylinder wall during the upward movement of the piston during the compression stroke, causing pulsation in the discharged refrigerant gas flow. Focus on the specific noise frequency that is causing these vibrations and noise.
Noise can be easily reduced using the existing valve plate.

According to the present invention, the noise due to the pulsation can be reduced without requiring any special device or equipment, and without increasing the size of the compressor.
It is an object of the present invention to provide an inexpensive reciprocating compressor that can be reduced by providing a structure for noise reduction in the structure of an existing compressor.

The present invention can reduce the noise due to the pulsation, and in the past, the loss due to the flow of the medium was large in a muffler or the like, but it was possible to reduce the cost of the reciprocating motion without lowering the performance of the compressor at all. Mold compressor was obtained.

According to the present invention, noise due to pulsation can be reduced by providing a space portion to which the damping effect of the Helmholtz resonator is applied to an existing valve plate without specially requiring a device or apparatus and without increasing the size of the compressor. And a reciprocating compressor having an inexpensive configuration.

Further, the resonance chamber, which is a space provided in the valve plate to which the damping action of the Helmholtz resonator is applied, is provided in a portion closed by the discharge valve and the suction valve. The formation of the resonance chamber can be formed simply by providing an open recess or a through hole, and the formation is extremely simple and inexpensive.

Further, in a resonance chamber which is a space provided in a valve plate to which the damping action of the Helmholtz resonator is applied, a portion other than the resonance chamber provided in a portion closed by a discharge valve and a suction valve is also provided. Since the resonance chamber can be provided, the valve plate can be effectively used.

Further, in the present invention, attention is paid to the frequency of a specific noise caused by the generation of the pulsating operation of the suction valve by the cooling gas sucked from the suction chamber into the suction hole of the valve plate. Can also be reduced. That is, it is possible to reduce not only the noise due to the pulsation on the discharge side but also the noise due to the pulsation of the suction valve, without compromising the performance of the compressor. A reciprocating compressor can be obtained.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of an upper part of a compressor for explaining related structures of a cylinder head, a suction chamber, a valve plate, a valve, and the like of the compressor.

FIG. 2 is an enlarged sectional view of a portion A in FIG. 1, showing one embodiment of the compressor of the present invention.

FIG. 3 is a cross-sectional view showing another embodiment of the compressor of the present invention and showing an explanation related to its manufacture.

FIG. 4 is a plan view of an embodiment of the compressor of the present invention.

FIG. 5 is a sectional view showing another embodiment of the compressor of the present invention.

FIG. 6 is a cross-sectional view illustrating a structure of a reciprocating compressor applied to the present invention.

FIG. 7 is a diagram illustrating the principle of a Helmholtz resonator.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Compressor (variable capacity) 2 Compressor casing 3 Front housing 4 Cylinder block 4a Notch groove part 5 Cylinder head 6 Valve plate 7 Cylinder gasket 8 Drive shaft 10 Piston 11, 12 Through hole part 13, 14 Bearing 15 Drive shaft support member 16 Cylinder 17 Crank chamber 18 Rotor 19 Rotation stop pin 21 Swash plate boss 22 Swing plate 23 Piston rod 24, 25 Ear 24a Engagement pin 25a Long hole 26, 27 Bearing 28 Plate-shaped guide member 31 Suction hole 32 Suction Valve 33 Valve receiving portion (recess) 34 Discharge hole 35 Discharge valve 36 Retainer 41 Partition wall 42 Suction chamber 43 Discharge chamber 60 to 63 Resonance chamber 600 Hole 601, 602, 603 Pressure introducing section 650 Fixing bolt

Continuing on the front page (72) Inventor Yoshinobu Ichikawa, 20 Kotobukicho, Isesaki-shi, Gunma Sanden Co., Ltd. (72) Inventor Tatsuto 20 Kotobukicho, Isesaki-shi, Gunma Sanden Co., Ltd. F-term (reference) 3H003 AA03 AC03 BA01 CC12

Claims (5)

[Claims] 1. A reciprocating system in which a rotational driving force transmitted from an external drive source to a drive shaft is transmitted to a piston via a crank mechanism, and a cooling gas sucked from outside is sucked and compressed by the piston and circulated to an air conditioning system. In the dynamic compressor, a front housing in which the drive shaft is rotatably mounted, as a constituent member of a housing serving as a pressure vessel, a cylinder block including a cylinder connected to the front housing and accommodating the piston, A valve plate connected to the cylinder block, to which a suction valve for sucking cooling gas supplied from the outside toward the bottom dead center side of the piston into the cylinder is attached; and To discharge the cooling gas compressed by the suction chamber and the piston to the outside of the suction chamber for supplying the cooling gas supplied from the suction valve to the suction valve. A cylinder head or the like having a discharge chamber formed therein, wherein a resonance chamber comprising a space portion to which the damping action of the Helmholtz resonator is applied is provided on the valve plate, and the pressure introduction portion of the resonance chamber communicates with the discharge side. A reciprocating compressor. 2. A resonance chamber which is a space provided in a valve plate to which the damping action of the Helmholtz resonator is applied, wherein the resonance chamber is provided in a portion closed by a discharge valve and a suction valve. The reciprocating compressor according to claim 1, wherein 3. A resonance chamber which is a space provided in a valve plate to which the damping action of the Helmholtz resonator is applied, wherein the resonance chamber has a through hole, and the hole has a discharge valve, a suction valve, The reciprocating compressor according to claim 2, wherein the compressor is provided in a portion closed by: 4. In a resonance chamber which is a space provided in a valve plate to which the damping action of the Helmholtz resonator is applied, a portion other than the resonance chamber provided in a portion closed by a discharge valve and a suction valve is provided. 3. The reciprocating compressor according to claim 2, further comprising another resonance chamber. 5. A resonance chamber, which is a space provided in a valve plate to which the damping action of the Helmholtz resonator is applied, wherein a resonance chamber in which a pressure introduction part communicates with a discharge side is provided, and the pressure introduction part is a discharge side or a suction side. The reciprocating compressor according to claim 1 or 4, further comprising another resonance chamber communicating with the side.