JP2590662Y2 - Reciprocating compressor - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a reciprocating compressor used in a vehicle air conditioner or the like.

[0002]

2. Description of the Related Art Conventionally, for example, Japanese Patent Application Laid-Open No. 60-175783.
A compressor that compresses refrigerant gas by reciprocating each piston in a plurality of bores formed in a cylinder block in parallel with a drive shaft is known, such as a swash plate compressor described in Japanese Patent Application Laid-Open Publication No. H11-163,837. . In this type of compressor, a drive shaft is fitted and supported in a center shaft hole of a cylinder block, and each piston is linked to a swash plate in a crank chamber that cooperates with the drive shaft to move directly in each bore. A housing is joined to the end surface of the cylinder block via a valve plate.
A discharge chamber is provided in a central area, and a suction chamber is provided in an outer peripheral area so as to communicate with each bore. Refrigerant gas is sucked into the suction chamber from an external refrigeration circuit via a refrigerant introduction hole provided in the outer peripheral wall of the housing. In addition, a suction port and a discharge port are formed in the valve plate corresponding to each bore,
A suction valve and a discharge valve are provided at these suction port and discharge port, respectively.

[0003] When the swash plate rotates with the driving of the drive shaft, each piston reciprocates in the bore, whereby refrigerant gas is sucked into the bore from the suction chamber, and the refrigerant gas is compressed and discharged. Discharged into the chamber. In this type of compressor, the pulsation of the suction pressure has conventionally been a problem. This suction pulsation is caused by a change in pressure of the refrigerant gas due to a change in the passage area when the refrigerant gas passes through the refrigerant introduction hole, the suction chamber, and the suction port of the valve plate during the suction stroke. Therefore, the noise is transmitted to an evaporator in the vehicle cabin through a pipe, and causes abnormal noise.

Accordingly, Japanese Utility Model Laid-Open Publication No. Sho 61-145888 discloses a compressor in which a suction pulsation is reduced by partitioning the suction chamber in the axial direction by a partition wall to provide a muffler effect. In this compressor, the suction chamber communicates with the refrigerant introduction hole through which the refrigerant gas is introduced from the external refrigeration circuit by the partition wall, and the through hole formed through the first suction chamber and the partition wall. And a second suction chamber which communicates with the bore through a suction port of the valve plate, and the muffler effect in the second suction chamber can reduce suction pulsation.

[0005]

However, even in the conventional compressor in which the suction chamber is divided in the axial direction, it is difficult to sufficiently reduce the suction pulsation. It could not be prevented reliably. The present invention has been made in view of the above circumstances, and has as a technical problem to be solved to further reliably prevent generation of abnormal noise due to suction pulsation by further improving a suction chamber formed in a housing. It is.

[0006]

According to the present invention, there is provided a cylinder block having a plurality of bores parallel to an axis, a drive shaft fitted and supported in a shaft hole of the cylinder block, and A piston linked to a swash plate cooperating with a drive shaft and linearly moving in the bore; a housing joined to an outer end of the cylinder block via a valve plate; and a housing formed in the housing and penetrating through the valve plate. A reciprocating compressor having a suction chamber that communicates with the bore through a suction port provided, wherein the suction chamber is separated from a first suction chamber that communicates with a refrigerant introduction hole by a partition that divides the suction chamber in an axial direction. A second suction chamber that communicates with the suction port, and the second suction chamber is further divided into small chambers that communicate with each suction port independently by a partition wall that partitions the second suction chamber in the circumferential direction. Each said chamber was penetrated by the said partition It employs a novel means of which communicates with the first suction chamber via the hole.

Further, in the present invention, it is possible to adopt a means for suspending the suction port and the through hole as much as possible in the axial projection plane for each of the small chambers.

[0008]

When the reciprocating compressor of the present invention is driven, the piston is reciprocated by the rotation of the drive shaft and the swash plate, and is formed in the housing through a suction port provided through the valve plate. Refrigerant gas is sucked into the bore from the suction chamber. In the compressor according to the present invention, the suction chamber is divided into a first suction chamber communicating with the refrigerant introduction hole and a second suction chamber communicating with the suction port by a partition partitioning the suction chamber in the axial direction. The chamber is further divided into small chambers that communicate with the respective suction ports independently by a separating plate that partitions the chambers in the circumferential direction, and each of the small chambers is connected to the first suction chamber through a through hole formed in the partition. Has been communicated with. Therefore, at the time of the suction stroke, the refrigerant gas from the external refrigeration circuit first enters the first suction chamber through the refrigerant introduction hole, and then sequentially passes through the through hole of the partition wall as the second suction chamber. The liquid enters the small chamber and is sequentially sucked into each bore from this small chamber through the inlet of the valve plate. However, since the second suction chamber is divided into small chambers for each bore, interference with other bores occurs. The independent muffler effect without the pressure can more reliably reduce the suction pulsation.

In the compressor according to the present invention, when the suction port and the through hole are suspended as much as possible in the axial projection plane for each of the small chambers, the refrigerant passing through the small chambers The path length of the gas is lengthened, and the muffler effect is increased accordingly, so that the suction pulsation can be more reliably reduced.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is embodied in a variable displacement swash plate type compressor will be described below with reference to the drawings. FIG. 1 shows a cross-sectional view along the axial direction of the compressor according to the present embodiment, and FIG. 2 shows a cross-sectional view along a direction perpendicular to the axis taken along line AA in FIG. In the figure, reference numeral 1 denotes a cylinder block which constitutes a part of an outer shell of a compressor. A front housing 2 is joined to a front end of the cylinder block 1, and a rear housing 3 is provided with a valve plate 4 at a rear end. Are joined through. A drive shaft 6 penetrates a crank chamber 5 formed by the cylinder block 1 and the front housing 2, and the drive shaft 6 is rotatably mounted on the cylinder block 1 and the front housing 2 via a bearing 7. It is supported. Six bores 8 are formed in the cylinder block 1 around the axis and parallel to the axis.
The piston 9 is fitted in each of them.

A rotary support 10 is supported on the drive shaft 6 in the crank chamber 5 so as to be able to rotate synchronously with the drive shaft 6, and a spherical sleeve 11 is rotatably and slidably supported. The spherical sleeve 11 is urged rearward by a pressing spring 12 mounted on the outer periphery of the drive shaft 6. On the spherical sleeve 11, a spherical sleeve 11
A swash plate 14 formed in an annular shape so as to surround the swash plate is supported to be able to swing back and forth.

A hemispherical shoe 15 is engaged with both surfaces of the outer peripheral portion of the swash plate 14, and the outer surface of the shoe 15 is formed on the swash plate passage groove 9a formed in the neck of the piston 9 so as to face each other. Engaged with the support surface. Thus,
A plurality of pistons 9 moored to the swash plate 14 via shoes 15 are accommodated in each bore 8 so as to be able to reciprocate. A pair of arms 17 project from the upper rear surface of the swash plate 14 at symmetrical positions with respect to the drive shaft 6. on the other hand,
A pair of support arms 18 projecting rearward are provided on the upper portion of the rotary support 10 so as to face the pair of arm portions 17. A guide pin 21 whose lower end is slidably fitted to each arm portion 17 is mounted.

A discharge chamber 23 communicating with the bore 8 is formed in a central area on the front end face side of the rear housing 3, and a suction chamber 3 is formed in the rear housing 3 on the outer peripheral side of the discharge chamber 23.
0 is formed. The discharge chamber 23 communicates with the bore 8 through a discharge port 24 and a discharge valve 25 formed through the valve plate 4, and is formed through the outer peripheral wall of the rear housing 3 so that refrigerant gas flows to an external refrigeration circuit. Is communicated with a refrigerant discharge hole (not shown) for discharging air. On the other hand, the suction chamber 30 has a first suction chamber 3 communicating with a refrigerant introduction hole 26 through which a refrigerant gas is introduced from an external refrigeration circuit by a partition wall 31 partitioning the suction chamber 30 in the axial direction.
2 and a second suction chamber 33 communicating with a suction port 27 provided through the valve plate 4. The suction port 27 is provided with a suction valve 28. The second suction chamber 33 is further divided into small chambers 33a to 33f that are independently communicated with the respective suction ports 27 by separating walls 34 that partition the second suction chamber 33 in the circumferential direction.
Is communicated with the first suction chamber 32 through a through hole 35 penetrating therethrough. The suction port 27 and the normal 35
Are suspended as much as possible in the axial projection plane for each of the small chambers 33a to 33f. The rear housing 3 is equipped with a pressure control valve (not shown) for adjusting the pressure in the crank chamber 5.

In the compressor configured as described above,
When the swash plate 14 rotates with the rotation of the drive shaft 6, the swash plate 14 moored with each piston 9 slides in the circumferential direction with respect to the spherical sleeve 11 and swings. Reciprocate in bore 8. As a result, the refrigerant gas in the suction chamber 30 that has returned from the external refrigeration circuit via the refrigerant introduction hole 31 is supplied to the suction port 27 in the bore 8 whose volume is being expanded.
The refrigerant gas is sucked through the suction valve 28 and is discharged to the discharge chamber 23 through the discharge port 24 and the discharge valve 25 while being compressed. At this time, the discharge capacity of the refrigerant gas discharged to the discharge chamber 23 is controlled by adjusting the pressure in the crank chamber 5 by the pressure control valve. Then, the refrigerant gas in the discharge chamber 23 is sent out to a refrigeration circuit through a refrigerant discharge hole (not shown).

In the compressor of this embodiment, the suction chamber 3
0 is partitioned into a first suction chamber 32 that communicates with the refrigerant introduction hole 26 and a second suction chamber 33 that communicates with the suction port 27 by a partition wall 31 that partitions the second suction chamber 33 in the axial direction. Each of the suction ports 2 is separated by a separation plate 34 that divides this in the circumferential direction.
Each of the small chambers 33a to 33f communicates with the first suction chamber 32 through a through hole 35 formed through the partition wall 31. For this reason, at the time of the suction stroke, the refrigerant gas from the external refrigeration circuit first passes through the refrigerant introduction hole 26,
The suction chamber 32 enters the suction chamber 32, and then sequentially enters the small chambers 33 a to 33 f as the second suction chamber 33 through the through hole 35 of the partition wall 31, and sequentially enters the small chambers 33 a to 33 f through the suction port 27 of the valve plate 4. Is sucked into each bore 8, but the second
Since the suction chamber 33 is divided into the small chambers 33a to 33f for each of the bores 8, the suction pulsation can be more reliably reduced by an independent muffler effect without interference by other bores.

In the compressor of the present embodiment, the through hole 34 of the partition 31 and the suction port 27 of the valve plate 4
３３33f, the path length of the refrigerant gas passing through the small chambers 33a〜33f is increased, and the muffler effect is also increased, so that the suction is more reliably performed. Pulsation can be reduced. Therefore,
The compressor of the present embodiment can more reliably prevent the generation of abnormal noise due to suction pulsation.

(Evaluation of Characteristics) The compressor of the present embodiment was evaluated for characteristics as follows. The suction pulsation flows from the suction port 27 to the second suction chamber 33,
The heat is transmitted to the first suction chamber 32 and the refrigerant introduction hole 26. Therefore, input the sound pressure from the speaker through the inlet 27,
The sound pressure was measured at the inlet 27 and the refrigerant introduction hole 26, and the transfer function was obtained. Then, the amplitude of the output sound pressure was determined from the transfer function as the characteristic evaluation item. The result is shown in FIG.

For comparison, the compressor of Comparative Example 1 has the same structure as the compressor of the above embodiment except that the suction chamber 30 is a single suction chamber without the partition wall 31 and the separation wall 34.
The characteristics of the compressor of Comparative Example 2 having the same configuration as that of the compressor of the above embodiment except that the second suction chamber 33 is a single suction chamber without the separation wall 34 were also evaluated. FIG. 4 shows the evaluation result of the compressor of Comparative Example 1, and FIG. 5 shows the evaluation result of the compressor of Comparative Example 2.

As is clear from FIGS. 3 to 5, the compressor of this embodiment is transmitted from the suction port 27 to the refrigerant inlet 26 as compared with the compressors of Comparative Examples 1 and 2. It can be seen that the suction pulsation is significantly reduced. In the above-described embodiment, an example in which the discharge chamber 23 is formed on the inner peripheral side of the rear housing 3 and the suction chamber 30 is formed on the outer peripheral side of the discharge chamber 23 has been described. The present invention can be applied to a compressor in which the discharge chamber 23 is formed on the outer peripheral side of the chamber 30.

The swash plate type compressor of the above embodiment is of a variable displacement type. The swash plate 14 is fixed to the drive shaft 6 at a predetermined inclination angle, and the pressure of the piston 9 is changed by changing the pressure in the crank chamber 5. The present invention can also be applied to a fixed displacement swash plate type compressor configured to operate at a predetermined discharge displacement without adjusting the stroke.

[0021]

According to the compressor of the present invention, the suction chamber is divided into a first suction chamber and a second suction chamber by a partition partitioning the suction chamber in the axial direction, and the second suction chamber further surrounds the first suction chamber and the second suction chamber. Separated in the direction, the partition is divided into small chambers that communicate with each suction port independently, so the independent muffler effect corresponding to each bore in each small chamber can more reliably reduce suction pulsation. it can.

When the suction port and the through hole of the partition wall are suspended as much as possible in the axial projection plane for each small chamber, the path length of the refrigerant gas passing through the small chamber is extended. The muffler effect is also increased, and the suction pulsation can be more reliably reduced. Therefore, when the compressor of the present invention is applied to a vehicle cooling device, it is possible to effectively suppress abnormal noise and vibration generated by being transmitted from a suction chamber of the compressor to an evaporator or the like in a vehicle cabin through a pipe. It becomes possible.

[Brief description of the drawings]

FIG. 1 is a sectional view taken along an axial direction of a compressor according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view of the compressor taken along line AA of FIG. 1 in a direction perpendicular to the axis.

FIG. 3 is a diagram showing characteristics evaluation results of the compressor of the embodiment.

FIG. 4 is a diagram showing characteristics evaluation results of the compressor of Comparative Example 1.

FIG. 5 is a diagram showing characteristics evaluation results of the compressor of Comparative Example 2.

[Explanation of symbols]

1. Cylinder block 3. Rear housing 5.
Crank chamber 6 Drive shaft 8 Bore 9 Piston 14 Swash plate 23 Discharge chamber 27 Suction port 30 Suction chamber 31 Partition wall 32
... first suction chamber 33 ... second suction chamber 33a-33f ... small chamber 34 ...
Separation wall 35 ... through hole

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Tetsushi Komura 2-1-1, Toyota-cho, Kariya-shi, Aichi Pref. Inside the Toyota Industries Corporation (56) References Japanese Utility Model 6-158458 (JP, U) (58) Field surveyed (Int.Cl. ⁶ , DB name) F04B 27/08

Claims (2)

(57) [Scope of request for utility model registration] A cylinder block having a plurality of bores parallel to an axis, a drive shaft fitted and supported in a shaft hole of the cylinder block, and a swash plate cooperating with the drive shaft. A piston that moves directly in the bore, a housing joined to the outer end of the cylinder block through a valve plate, and communicates with the bore through a suction port formed in the housing and penetrating through the valve plate. In a reciprocating compressor having a suction chamber, the suction chamber is divided into a first suction chamber communicating with a refrigerant introduction hole and a second suction chamber communicating with the suction port by a partition that partitions the suction chamber in the axial direction. The second suction chamber is further divided into small chambers that communicate with the respective suction ports independently by separating walls that partition the second suction chamber in the circumferential direction, and each of the small chambers is a through hole formed in the partition wall. Is communicated with the first suction chamber via Reciprocating compressor, wherein the door. 2. The reciprocating compressor according to claim 1, wherein the suction port and the through-hole are suspended as much as possible in an axial projection plane for each of the small chambers.