JP3203888B2 - 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 a reciprocating compressor suitable for a vehicle air conditioner, for example.

[0002]

2. Description of the Related Art A compressor of a type in which a plurality of bores are formed in a cylinder block, and a piston fitted in each of the bores is reciprocated with a predetermined phase difference through a swash plate, is a swing plate. It is well-known as a mold, a swash plate mold and the like, and is frequently used in, for example, a vehicle air conditioner.

[0003] In this type of compressor, the pulsation of the discharge pressure has conventionally been a problem. In the case of a vehicle air conditioner, the discharge pulsation is transmitted to the condenser through a pipe, and the condenser and its surroundings are transmitted. Vibration of the piping causes abnormal noise in the passenger compartment. Generally, the discharge pulsation transmitted from the discharge chamber to the pipe includes a direct component transmitted directly from the bore to the pipe,
There is an indirect component having a certain frequency distribution that is complicatedly generated in the discharge chamber depending on the shape of the discharge chamber. The former direct component generates a greater noise as the discharge pulsation occurs from the bore closer to the pipe. The latter indirect component, if the natural frequency of the vehicle frame or the like matches the above frequency band,
A resonance phenomenon is caused to amplify abnormal noise.

[0004] In order to suppress the generation of abnormal noise due to the vibration of the condenser, a muffler is conventionally provided in a pipe connecting the discharge chamber of the compressor and the condenser.

[0005]

However, the muffler mounted on the pipe as described above increases the installation space in the vehicle, and it is difficult to install the muffler in the engine room of a recent high-density vehicle. Is coming. Therefore,
Using the fact that the discharge pulsation is inversely proportional to the volume of the discharge chamber,
It is conceivable to increase the volume of the discharge chamber with respect to the discharge volume of the bore without providing a muffler in the pipe. But,
If the discharge chamber is expanded, the physique of the compressor is correspondingly increased, and the installation space becomes a problem similarly to the measures for providing a muffler in the piping.

In the method for reducing the discharge pulsation only by the volume effect of the discharge chamber as described above, the direct component transmitted from the bore directly to the pipe (particularly, the pulsation from the bore close to the pipe).
Is transmitted to the pipes with little reduction, and if the indirect component matches the natural frequency of the equipment of the vehicle, it is expected to resonate with the vibration of the equipment and reduce the noise in the passenger compartment. Can not.

Also, the suction pulsation in the suction chamber is transmitted to the evaporator through the pipe, and causes the same problem as the discharge pulsation. The present invention has been made in view of the above circumstances, and has as an object to solve the problem of reducing discharge pulsation or suction pulsation without increasing the installation space. Another object of the present invention is to reduce or prevent a direct component transmitted from a bore directly to a pipe and an indirect component generated by the shape of a discharge chamber.

[0008]

According to one aspect of the present invention, there is provided a cylinder block having a plurality of bores arranged in parallel with an axis thereof, and a cylinder head for closing an outer end of the cylinder block with a valve plate interposed therebetween. In a compressor having a discharge chamber formed in the cylinder head, a sub-discharge chamber is provided in the cylinder block in an inner peripheral region from the plurality of bores, and the sub-discharge chamber is provided through a valve plate. The at least one through hole communicates with the discharge chamber.

In another aspect of the present invention, the auxiliary discharge chamber communicates with the discharge chamber through at least one inlet through hole provided in a valve plate, and communicates with the auxiliary discharge chamber. An outlet through-hole formed in the valve plate is connected to the discharge passage. In addition, the above embodiments are also applied to a compressor in which the arrangement of the discharge chamber and the suction chamber is exchanged, and the suction chamber is formed in the central area of the cylinder block and the discharge chamber is formed in the outer peripheral area.

In a preferred aspect, the sub-discharge chamber or the sub-suction chamber extends between the bores and is formed in a chain wheel shape.

[0011]

In the compressor according to the present invention in which the discharge chamber is formed in the cylinder head, the sub-discharge chamber communicates with the discharge chamber through at least one through hole formed in the valve plate. The sub-discharge chamber formed as described above has a substantial effect of expanding the volume of the discharge chamber, and can smooth discharge pulsation.

In the above aspect, when the through-hole acts as a throttle, the phase difference of the pressure wave generated between the refrigerant gas in the discharge chamber and the refrigerant gas in the sub-discharge chamber causes the phase difference through the through-hole. Interference is caused by the gas flow, and the peaks of the pressure waves cancel each other to further smooth the discharge pulsation. In another aspect of the present invention, since the discharge chamber and the sub-discharge chamber communicate with each other through the inlet through-hole, and the outlet through-hole of the multiple discharge chamber communicates with the discharge passage, all the refrigerant gas is discharged once. Since the refrigerant gas enters the sub-discharge chamber from the chamber and flows into the discharge passage, the volume expansion effect of the refrigerant gas when the refrigerant gas enters the discharge chamber from the bore through the discharge hole, and the auxiliary gas flows from the discharge chamber through the inlet through-hole. It effectively reduces the discharge pulsation in two stages, that is, the effect of expanding the volume when entering the discharge chamber. Therefore, even when the natural frequency of the equipment of the vehicle matches the indirect component generated by the shape of the discharge chamber, the resonance can be suppressed and the noise can be reduced.
Further, the phenomenon that the component directly from the bore is transmitted to the pipe is structurally avoided.

Similarly, in the compressor in which the suction chamber is formed in the cylinder head, if the former mode is adopted, the sub-suction chamber substantially increases the volume of the suction chamber and reduces the refrigerant gas in the suction chamber. The phase difference of the pressure wave generated between the refrigerant gas in the auxiliary suction chamber and the refrigerant gas in the sub suction chamber interferes with the gas flow through the through hole, so that the suction pulsation can be smoothed. In addition, if the latter aspect is adopted, for all the refrigerant gas, the effect of reducing the suction pulsation over two stages of the suction chamber and the sub suction chamber is achieved, and the effect of reducing the indirect component caused by the shape of the suction chamber and the like is achieved. The phenomenon that the component directly from the bore is transmitted to the pipe is structurally avoided.

When the sub-discharge chamber or the sub-suction chamber is formed in the form of a chain wheel, the volume of the discharge chamber or the suction chamber can be expanded more effectively.

[0015]

According to one aspect of the present invention, a plurality of bores communicate with a discharge chamber or a suction chamber in a cylinder block through a sub-discharge chamber or a sub-suction chamber provided in a cylinder block in an inner peripheral area. Therefore, the through hole and the sub-discharge chamber perform a muffler function with the discharge chamber, or the through hole and the sub-suction chamber also perform a muffler function with the suction chamber, and pulsation is markedly increased. Therefore, the generation of vibration and abnormal noise of the piping system can be favorably reduced.

Further, in another aspect of the present invention, for all the refrigerant gas, the effect of expanding the volume when the refrigerant gas enters the discharge chamber from the bore via the discharge hole, and the effect of the secondary discharge from the discharge chamber via the inlet through-hole. The discharge pulsation is reduced in two stages, that is, the volume expansion effect when entering the room, to prevent the resonance phenomenon between the indirect component of the discharge pulsation or the suction pulsation and the vibration of the equipment of the vehicle, and the discharge pulsation or the suction pulsation. Direct components can be blocked.

[0017]

1 and 2 show a rotary swash plate type compressor embodying the present invention. However, the present invention is not limited to the above-described type of compressor, but can be applied to all reciprocating compressors. In FIG. 1, a front end of a cylinder block 1 that forms an outer shell of the compressor includes:
The housing 2 in which the crank chamber 2a is formed is connected,
At the rear end, a discharge chamber 3b is provided in a central area, and a suction chamber 3a is provided in an outer peripheral area.
Is connected via a valve plate 4.

In the cylinder block 1 supporting the drive shaft 5 together with the housing 2, five bores 1a are formed in parallel with the central shaft hole 1b into which one end of the drive shaft 5 is inserted. The piston 6 is fitted so that it can slide back and forth. The rotating base 7 is fixed to the drive shaft 5 in the crank chamber 2a.
The swash plate 9 is connected to the drive shaft 5 and is rotatably supported by a left and right pivot 9b (only one is shown) of a sleeve 9a loosely fitted on the drive shaft 5. A swing plate 11 whose rotation is restricted by a through bolt 10 is supported on the rotary swash plate 9, and the swing plate 11 is connected to the piston 6 via a connecting rod 12.

The valve plate 4 is formed with a suction hole 4a and a discharge hole 4b for communicating the bore 1a with the suction chamber 3a and the discharge chamber 3b, respectively. Is connected to a discharge valve 14 via a retainer 15. The reed 13 a formed in the suction valve 13 opens and closes the suction hole 4 a in response to the reciprocating motion of the piston 6. Similarly, the reed 14 a formed in the discharge valve 14 causes the discharge hole 4 b to It opens and closes in response to reciprocation.

The above is the configuration of the ordinary rotary swash plate type compressor, in which the rotational motion of the drive shaft 5 is transmitted through the rotary swash plate 9 to the swing plate 1.
As the piston 6 reciprocates in the bore 1a, the refrigerant gas sucked into the bore a from the suction chamber 3a is discharged into the discharge chamber 3b while being compressed.
Then, the stroke of the piston 6 and the tilt angle of the swinging plate 11 change according to the pressure difference between the crank chamber pressure and the suction chamber pressure,
The discharge gas volume is controlled.

By the way, in the compressor of this embodiment, the bore 1
a sub-discharge chamber 1
6 are formed. As shown in FIG. 2, the sub-discharge chamber 16 extends from a central area 16a of the cylinder block 1 where the central shaft hole 1b is closed halfway by the end of the drive shaft 5 to a sandwich area 16b of each bore 1a. It extends to form a chain wheel, and the volume is increased as much as possible. And
The sub-discharge chamber 16 communicates with the discharge chamber 3b via a through hole 17 formed in the valve plate 4 and the suction valve 13. Here, the through hole 17 is provided in a circular shape at an arbitrary position in a circumferential direction with the axis as a base point. The cross-sectional area of the through-hole 17 is not particularly limited, but is set to be sufficiently smaller than the cross-sectional area of the discharge chamber 3b and the sub-discharge chamber 16 in order to have a function as a throttle. However, the number of the through holes 17 is not limited to one, and a plurality of the through holes 17 can be provided.

In the compressor having the above-described structure, a discharge pulsation occurs in the discharge chamber 3b due to the reciprocation of the piston 6, and due to a change in the pressure in the discharge chamber 3b due to the pulsation, the refrigerant gas in the discharge chamber 3b becomes Through hole 17 as aperture
And interfere with the refrigerant gas in the sub-discharge chamber 16.
That is, when the pressure of the discharge chamber 3 b becomes higher than the pressure of the sub-discharge chamber 16 due to the discharge pulsation, the refrigerant gas in the discharge chamber 3 b flows into the sub-discharge chamber 16 through the through hole 17. Therefore, the upper peak of the pressure wave in the discharge chamber 3b is suppressed to a low value. On the other hand, the pressure of the sub-discharge chamber 16 rises due to the inflow of the refrigerant gas from the discharge chamber 3b, and the discharge chamber 3
When the pressure becomes higher than the pressure b, the refrigerant gas flows out from the sub-discharge chamber 16 to the discharge chamber 3b. Thereby, the lower peak of the pressure wave in the discharge chamber 3b is increased. FIG. 3 shows the pressure waves of the discharge chamber 3b and the sub-discharge chamber 16 that interfere with each other, the solid line indicates the pressure wave of the discharge chamber 3b, and the broken line indicates the pressure wave of the sub-discharge chamber 16.

As described above, since the discharge chamber 3b and the sub-discharge chamber 16 communicate with each other through the through hole 17, the pressure wave in both chambers is reduced.
The pressure waves in the sub-discharge chamber 16 interfere with each other with a phase difference slightly delayed from the pressure wave in the discharge chamber 3b. Such out-of-phase interference of both pressure waves pushes each other's upper peak down,
It acts to raise the lower peak and performs the function of smoothing the discharge pulsation. Therefore, the pulsation of the discharge chamber 3b that vibrates the condenser and its surroundings is smoothed, and the noise in the vehicle compartment can be reduced.

In general, the discharge pulsation has the following relationship between the bore discharge volume and the discharge chamber volume. Therefore, the discharge pulsation ∝ bore discharge volume / discharge chamber volume By making the volume as large as possible by forming a chain wheel, the pressure of the sub-discharge chamber 16 indicated by the dotted line in FIG. 3 is further reduced in amplitude, and the discharge pulsation can be further smoothed. Understand.

When a plurality of through holes 17 are provided, some of them can be provided with leads using the suction valve 13. With such a configuration, when the discharge chamber pressure rises, the lead opens greatly, and the upper peak of discharge pulsation is reduced by the effect of expanding the volume of the discharge chamber 3b. On the other hand, when the discharge chamber pressure decreases, the flow rate of the refrigerant gas returning from the sub-discharge chamber 16 to the discharge chamber 3b becomes slow, and the lower peak of the pressure wave in the sub-discharge chamber becomes higher than in the embodiment of FIG. For this reason, the refrigerant gas in both chambers interferes so that the lower peak of the discharge pulsation is further lifted. FIG. 4 shows pressure waves in the discharge chamber 3b and the sub-discharge chamber 16 in this case.

The present invention can be used not only for smoothing discharge pulsation but also for smoothing suction pulsation. FIG. 5 shows a configuration of a compressor for reducing suction pulsation, and members having the same functions as those in FIG. 1 are denoted by common reference numerals. In this compressor, the piston 6 is reciprocated by a rotary swash plate 20, and a suction chamber 3a is formed in a central area of the cylinder head 3, and a discharge chamber 3b is formed in an outer peripheral area of the cylinder head 3. And cylinder block 1
A sub-suction chamber 18 is formed in a chain wheel shape extending between a central region formed by closing the center shaft hole 1b on the way and a region between the bores 1a. The sub suction chamber 18 has a through hole 19 formed in the valve plate 4 and the suction valve 13 similarly to the embodiment of FIG.
Through the suction chamber 3a.

In such a compressor, the suction chamber 3a
Can be smoothed by the same principle as in the embodiment of FIG. In each embodiment, the sub-discharge chamber 16 or the sub suction chamber 18 is formed so as to include the central area of the cylinder block 1 in which the central shaft hole 1b is closed halfway. When the auxiliary discharge chamber 16 extends to the end face of the sub-discharge chamber 16 around the central shaft hole 1b.
Alternatively, the sub suction chamber 18 is formed. Even with such a configuration, there is an effect of smoothing the discharge pulsation or the suction pulsation.

As described above, in the compressor in which the central shaft hole 1b extends to the end face of the cylinder block 1 and the sub-discharge chamber 16 or the sub-suction chamber 18 is formed therearound, a chain wheel-shaped auxiliary discharge is provided. By making the hollow portion corresponding to the valley portion of the chamber 16 or the sub suction chamber 18 function as a throttle, interference action of the refrigerant gas occurs between the hollow portions corresponding to the peak portions protruding between the bores, and further discharge pulsation occurs. Alternatively, an effect of smoothing suction pulsation can be produced.

Next, still another embodiment of the present invention will be described with reference to FIG. The embodiment shown in FIG. 6 is similar to the compressor in FIG.
b, a cylinder head 3 having a suction chamber 3a formed in the outer peripheral area
Are connected via a valve plate 4. A sub-discharge chamber 21 in the form of a chain wheel is formed by drilling the cylinder block 1 in the inner peripheral area from the bore 1a.

The present embodiment is characterized in that, in addition to having an inlet through-hole 22 for communicating the sub-discharge chamber 21 and the discharge chamber 3b, it is connected to the sub-discharge chamber 21 and directly connected to the discharge passage 24 of the compressor. It has an outlet hole 23 which is provided. More specifically, the inlet plate 22 and the valve plate 4 and the suction valve 1 are located at arbitrary positions in the circumferential direction with respect to the axial center, similarly to the through hole 17 in the embodiment of FIG.
3, one is formed in a circular hole shape, and the cross-sectional area thereof is also the discharge chamber 3b.
And the cross-sectional area of the sub-discharge chamber 21 is set sufficiently small. On the other hand, the outlet through-hole 23 is formed in the valve plate 4 and the suction valve 13 on the same circumference as the inlet through-hole 22, for example.
It communicates with a discharge port 25 formed in the end face of the cylinder head 3 through a discharge passage 24 made of a pipe material extending inside the inside b. The discharge passage 24 may be formed by forming the cylinder head 3 into a concave shape toward the valve plate 4.

Accordingly, in the compressor having the above structure, all the refrigerant gas in the bore 1a expands once when discharged from the discharge hole 4b into the discharge chamber 3b, and then expands from the discharge chamber 3b through the inlet through hole 22 to the sub-hole. When it is discharged into the discharge chamber 21, it expands again. This is similar to the principle of an inflatable muffler in an automobile, in which the pressure wave peak is reduced twice. Therefore, also in the present embodiment, similarly to the embodiment in FIG. 1, the discharge pulsation that vibrates the piping system is suppressed, and the abnormal noise in the vehicle compartment can be reduced favorably.

In particular, in this embodiment, even when the indirect component caused by the shape of the discharge chamber 3b or the like and the natural frequency of the equipment of the vehicle match, the component of the specific band is reduced in the sub-discharge chamber 21. Therefore, it is possible to prevent a phenomenon that abnormal noise is caused by resonance with the equipment. In addition, each bore 1a
The discharge hole 4b and the discharge passage 24 are separated from each other through the sub-discharge chamber 16, so that there is no room for transmitting the direct component of the discharge pulsation to the pipe.

Therefore, the present embodiment has a better effect of reducing vibration and abnormal noise than the embodiment of FIG. FIG.
5 can also be applied to a compressor as shown in FIG. 5, that is, a compressor in which the arrangement of the discharge chamber and the suction chamber is interchanged, and the suction chamber is formed in the central area of the cylinder block and the discharge chamber is formed in the outer peripheral area. it can. In this case, the suction chamber and the sub suction chamber communicate with each other through an outlet hole formed in the valve plate 4 and the suction valve 13, and an inlet hole formed in the same manner communicates with the suction passage. According to such an embodiment, as in the case of the discharge pulsation, the direct component of the suction pulsation can be prevented and the indirect component can be reduced.

Also, in the embodiment of the compressor in which the arrangement of the discharge chamber and the suction chamber is exchanged, the number of outlet holes is not limited to one as in the case of the hole 17, and a plurality of outlet holes can be scattered. It is.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing the entire configuration of a compressor according to one embodiment of the present invention.

FIG. 2 is a side view of a cylinder block of the compressor.

FIG. 3 is a pressure waveform diagram of a discharge chamber and a sub discharge chamber when discharge pulsation is smoothed by the present invention.

FIG. 4 is a pressure waveform diagram of a discharge chamber and a sub discharge chamber when a lead is provided in a through hole according to the present invention.

FIG. 5 is a cross-sectional view showing the entire configuration of a compressor according to another embodiment of the present invention.

FIG. 6 is a cross-sectional view showing the entire configuration of a compressor according to still another embodiment of the present invention.

[Explanation of symbols]

1 ... cylinder block, 1a ... bore, 2 ... housing,
3 ... Cylinder head, 3a ... Suction chamber, 3b ... Discharge chamber, 4
... valve plate, 4b ... discharge hole, 5 ... drive shaft, 6 ... piston, 1
3: suction valve, 16, 21: sub-discharge chamber, 17: through hole, 18
... a sub suction chamber, 19 ... a hole, 22 ... an inlet hole, 23 ... an outlet hole, 24 ... a discharge port.

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F04B 27/08

Claims (5)

(57) [Claims] A cylinder block having a plurality of bores arranged side by side in parallel with an axis; and a cylinder head for closing an outer end of the cylinder block with a valve plate interposed therebetween. In the compressor in which a chamber is formed, a sub-discharge chamber is provided in the cylinder block in an inner peripheral region from a plurality of bores, and the sub-discharge chamber is connected to the discharge port through at least one through hole formed in a valve plate. A reciprocating compressor characterized by communicating with a chamber. 2. A cylinder block having a plurality of bores juxtaposed in parallel with an axis, and a cylinder head for closing an outer end of the cylinder block with a valve plate interposed therebetween. In the compressor in which a chamber is formed, a sub-discharge chamber is provided in the cylinder block in an inner peripheral region from a plurality of bores, and the sub-discharge chamber is provided through at least one inlet through hole provided through a valve plate. A reciprocating compressor in which an outlet through hole formed in the valve plate to communicate with the discharge chamber and communicate with the sub-discharge chamber is connected to a discharge passage. 3. A cylinder block having a plurality of bores arranged side by side in parallel with an axis, and a cylinder head for closing an outer end of the cylinder block with a valve plate interposed therebetween. In the compressor in which a chamber is formed, a sub-suction chamber is provided in the cylinder block in an inner peripheral region from a plurality of bores, and the sub-suction chamber is provided with at least one suction hole through at least one through hole formed in a valve plate. A reciprocating compressor characterized by communicating with a chamber. 4. A cylinder block having a plurality of bores juxtaposed in parallel with an axis, and a cylinder head for closing an outer end of the cylinder block with a valve plate interposed therebetween. In the compressor in which a chamber is formed, a sub-suction chamber is provided in the cylinder block in an inner peripheral region from a plurality of bores, and the sub-suction chamber is formed through at least one outlet through hole provided through a valve plate. A reciprocating compressor wherein an inlet through hole formed in the valve plate is connected to a suction passage so as to communicate with the suction chamber and to communicate with the sub suction chamber. 5. The reciprocating compressor according to claim 1, wherein said sub-discharge chamber or sub-suction chamber extends between the bores and is formed in a chain wheel shape.