JPH0777157A - Reciprocating compressor - Google Patents

Abstract

PURPOSE:To reduce vibration in a piping system and abnormal noise in a car by reducing discharging and suctioning pulsative motion in a reciprocative compressor. CONSTITUTION:In a compressor, a discharge chamber 3b or a suction chamber 3a are formed in a cylinder head 3 connected to an outer end of a cylinder block 1 through a valve plate 4. A sub-discharge chamber 16 or a sub-suction chamber is formed in an inner peripheral area compared to a bore 1a of the cylinder block 1. The sub-discharge chamber 16 or the sub-suction chamber is communicated with the discharge chamber 3b or the suction chamber through at least one through-hole 17 formed on the valve plate 4. In another phase, an outlet through-hole or an inlet through-hole formed on the sub-discharge chamber or the sub-suction chamber is communicated with a discharge passage or a suction passage.

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, for example, a vehicle air conditioner.

[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 these bores is reciprocated with a predetermined phase difference via a swash plate is known as an oscillating plate. Type, swash plate type, etc., and is often used in, for example, a vehicle air conditioner.

In this type of compressor, the pulsation of the discharge pressure has conventionally been a problem, and in the case of a vehicle air conditioner, the above-mentioned discharge pulsation is transmitted to a condenser via a pipe, and the condenser and its surroundings. This may cause the pipe to vibrate and cause abnormal noise in the passenger compartment. Generally, in the discharge pulsation transmitted from the discharge chamber to the pipe, the 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 due to the shape of the discharge chamber. The former direct component produces more abnormal noise as the discharge pulsation generated from the bore closer to the pipe. The latter indirect component, if the natural frequency of the vehicle frame, etc. matches the above frequency band,
A resonance phenomenon is caused to amplify the abnormal noise.

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

[0005]

However, the muffler provided in the pipe as described above increases the installation space for the vehicle, and it becomes difficult to install the muffler in the engine room of a recent highly densified vehicle. Is coming. Therefore,
Utilizing that discharge pulsation is inversely proportional to the volume of the discharge chamber,
It is conceivable to expand 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 becomes larger, and the installation space becomes a problem as in the case where the muffler is installed in the pipe.

In the method of reducing the discharge pulsation only by the volume effect of the discharge chamber as described above, the direct component directly transmitted from the bore to the pipe (especially the pulsation from the bore close to the pipe)
Is transmitted to the pipe with almost no 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.

Further, the suction pulsation in the suction chamber is also 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 an object thereof is to reduce discharge pulsation or suction pulsation without increasing the installation space. Another problem to be solved by the present invention is to reduce or prevent a direct component that is directly transmitted from the bore to the pipe and an indirect component that is generated due to the shape of the discharge chamber and the like.

[0008]

SUMMARY OF THE INVENTION One aspect of the present invention is a cylinder block having a plurality of bores arranged in parallel with an axis and a cylinder head for closing an outer end of the cylinder block with a valve plate interposed therebetween. A compressor in which a discharge chamber is formed in the cylinder head, a sub-discharge chamber is provided in the cylinder block in an inner peripheral region of the plurality of bores, and the sub-discharge chamber penetrates the valve plate. The discharge chamber communicates with at least one through hole.

According to another aspect of the present invention, the sub-discharge chamber is communicated with the discharge chamber via at least one inlet passage hole penetrating the valve plate, and is communicated with the sub-discharge chamber. An outlet passage formed through the valve plate is connected to the discharge passage. Further, each of the above aspects is also applied to a compressor in which the positions of the discharge chamber and the suction chamber are exchanged, and the suction chamber is formed in the central region of the cylinder block and the discharge chamber is formed in the outer peripheral region.

Further, in a preferred mode, the auxiliary discharge chamber or the auxiliary suction chamber is formed in a chain wheel shape so as to extend between the bores.

[0011]

In the compressor in which the discharge chamber is formed in the cylinder head of the present invention, in the aspect in which the auxiliary discharge chamber is communicated with the discharge chamber through at least one through hole penetrating the valve plate, the cylinder block The sub-discharge chamber formed in 2) produces a substantial volume expansion effect of the discharge chamber and can smooth the discharge pulsation.

Further, in the above aspect, when the through hole is made to act 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 auxiliary discharge chamber passes through the through hole. The flow of gas interferes with each other, and the peaks of the pressure waves are canceled each other to further smooth the discharge pulsation. In another aspect of the present invention, the discharge chamber and the sub-discharge chamber communicate with each other via the inlet passage, and the outlet passage of the multiple discharge chamber communicates with the discharge passage, so that all the refrigerant gas is discharged once. Since it enters the discharge chamber from the chamber and flows into the discharge passage, the volume expansion effect of all the refrigerant gas when it enters the discharge chamber from the bore through the discharge hole and the auxiliary gas from the discharge chamber through the inlet through hole It effectively acts to reduce the discharge pulsation in two steps, namely, the volume expansion effect 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, it is possible to suppress resonance and reduce abnormal noise.
Further, the phenomenon that the direct component from the bore is transmitted to the pipe is structurally avoided.

Similarly, in the compressor having the suction chamber formed in the cylinder head, if the former mode is adopted, the sub-suction chamber substantially expands the volume of the suction chamber and the refrigerant gas in the suction chamber. The phase difference of the pressure wave generated with 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, the action of reducing the suction pulsation in two stages of the suction chamber and the sub-suction chamber for all the refrigerant gas is achieved, and the action of reducing the indirect component caused by the shape of the suction chamber and the like is achieved. Structurally avoid the phenomenon that the direct component from the bore is transmitted to the pipe.

If the auxiliary discharge chamber or the auxiliary suction chamber is formed in a chain wheel shape, the volume of the discharge chamber or the suction chamber can be expanded more effectively.

[0015]

According to one aspect of the present invention, the auxiliary discharge chamber or the auxiliary suction chamber provided in the cylinder block in the inner peripheral region of the plurality of bores communicates with the discharge chamber or the suction chamber in the cylinder block through the through hole. Therefore, the through hole and the auxiliary discharge chamber perform a muffler action with the discharge chamber, or the through hole and the auxiliary suction chamber similarly perform a muffler action with the suction chamber, resulting in a remarkable pulsation. As a result, the vibration of the piping system and the generation of abnormal noise are satisfactorily reduced.

Further, in another aspect of the present invention, for all the refrigerant gas, the volume expansion effect when the refrigerant gas enters the discharge chamber from the bore through the discharge hole, and the sub discharge from the discharge chamber through the inlet through hole. The discharge pulsation is reduced in two steps, including the volume expansion effect when entering the chamber, and the resonance phenomenon between the indirect component of the discharge pulsation or the suction pulsation and the vibration of the vehicle equipment is prevented, and the discharge pulsation or the suction pulsation The direct component of can be blocked.

[0017]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A rotary swash plate type compressor embodying the present invention is shown in FIGS. However, the present invention can be applied not only to the above-mentioned type compressor but also to all reciprocating compressors. In FIG. 1, at the front end of the cylinder block 1 that forms the outer shell of the compressor,
The housing 2 in which the crank chamber 2a is formed is joined,
At the rear end, the discharge chamber 3b is located in the central region and the suction chamber 3a is located in the outer peripheral region.
A cylinder head 3 formed with is connected via a valve plate 4.

The cylinder block 1 supporting the drive shaft 5 together with the housing 2 is formed with five bores 1a in parallel with the central shaft hole 1b into which one end of the drive shaft 5 is inserted, and in each bore 1a. Has a piston 6 reciprocally slidably fitted therein. The rotary base 7 is fixed to the drive shaft 5 in the crank chamber 2a, and the rotary base 7 and the pins 8 are attached.
A rotatable swash plate 9 which is connected via the drive shaft 5 and is swingable is supported by the left and right pivots 9b (only one is shown) of the 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.

Further, the valve plate 4 is formed with a suction hole 4a and a discharge hole 4b which respectively communicate the bore 1a with the suction chamber 3a and the discharge chamber 3b, and a suction valve 13 on the front side and a rear surface side. A discharge valve 14 is joined to the valve via a retainer 15. Then, the lead hole 13a formed in the suction valve 13 opens and closes the suction hole 4a in response to the reciprocating movement of the piston 6, and similarly, the lead hole 14a formed in the discharge valve 14 causes the discharge hole 4b to open in the piston 6. It is designed to open and close in response to reciprocating motion.

The above is the configuration of a normal rotary swash plate compressor, in which the rotary motion of the drive shaft 5 is transmitted through the rotary swash plate 9 to the oscillating plate 1.
When the piston 6 reciprocates in the bore 1a, the refrigerant gas sucked from the suction chamber 3a into the bore a is compressed and discharged into the discharge chamber 3b.
Then, the stroke of the piston 6 and the tilt angle of the oscillating 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 is formed. As shown in FIG. 2, the sub-discharge chamber 16 extends from the central region 16a of the cylinder block 1 formed by closing the central shaft hole 1b at the end of the drive shaft 5 to the interposing region 16b of each bore 1a. It extends to form a chain wheel, and the volume is expanded as much as possible. And
The sub discharge chamber 16 is communicated with the discharge chamber 3b through a through hole 17 formed in the valve plate 4 and the suction valve 13. Here, one through hole 17 is provided in the shape of a circular hole at an arbitrary position in the circumferential direction with the axial center 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 areas of the discharge chamber 3b and the sub discharge chamber 16 in order to have a function as a diaphragm. However, the number of the through holes 17 is not limited to one, and a plurality of through holes 17 may be scattered.

In the compressor having the above construction, the reciprocating motion of the piston 6 causes a discharge pulsation in the discharge chamber 3b. Due to the change in the pressure in the discharge chamber 3b due to this pulsation, the refrigerant gas in the discharge chamber 3b becomes Through hole 17 as a diaphragm
And the refrigerant gas in the sub discharge chamber 16 interferes with each other.
That is, when the pressure of the discharge chamber 3b becomes higher than the pressure of the sub-discharge chamber 16 due to the discharge pulsation, the refrigerant gas in the discharge chamber 3b 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 heading toward the lower peak.
When the pressure becomes higher than the pressure of b, the outflow of the refrigerant gas from the auxiliary discharge chamber 16 to the discharge chamber 3b occurs. As a result, 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 which interfere with each other, the solid line shows the pressure wave of the discharge chamber 3b, and the broken line shows the pressure wave of the sub discharge chamber 16.

As described above, by communicating the discharge chamber 3b and the sub-discharge chamber 16 with the through holes 17, the pressure waves in both chambers are
The pressure wave in the sub-discharge chamber 16 interferes with each other with a phase difference slightly behind the pressure wave in the discharge chamber 3b. Such out-of-phase interference of both pressure waves pushes down the upper peak of each other,
It acts to lift the lower peak and fulfills the function of smoothing the discharge pulsation. Therefore, the pulsation of the discharge chamber 3b that vibrates the condenser and its periphery is smoothed, and abnormal noise in the vehicle interior can be reduced.

Since the discharge pulsation generally has the following relationship between the bore discharge volume and the discharge chamber volume, discharge pulsation ∝ bore discharge volume / discharge chamber volume By forming it in a chain wheel shape and increasing the volume as much as possible, the pressure of the auxiliary discharge chamber 16 shown by the dotted line in FIG. 3 can be made smaller in amplitude, and the discharge pulsation can be further smoothed. Recognize.

When a plurality of through holes 17 are provided, some of them can be provided with reeds by utilizing the suction valve 13. With such a configuration, when the pressure in the discharge chamber rises, the lead largely opens, and the upper peak of the discharge pulsation is lowered by the volume expansion effect 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 that in the embodiment of FIG. Therefore, the refrigerant gases in both chambers interfere so that the lower peak of the discharge pulsation is further lifted. The pressure waves of the discharge chamber 3b and the sub discharge chamber 16 in this case are shown in FIG.

The present invention can be used not only for smoothing the discharge pulsation but also for smoothing the suction pulsation. FIG. 5 shows the structure of a compressor that reduces the suction pulsation, and members that perform the same functions as in FIG. In this compressor, a piston 6 is reciprocated by a rotary swash plate 20, and a suction chamber 3a is formed in the central region of the cylinder head 3 and a discharge chamber 3b is formed in the outer peripheral region of the cylinder head 3. And the cylinder block 1
The auxiliary suction chamber 18 is formed in a chain wheel shape extending over a central region formed by closing the central shaft hole 1b on the way and a region between the bores 1a. The auxiliary suction chamber 18 has a through hole 19 formed in the valve plate 4 and the suction valve 13 as in the embodiment of FIG.
Is communicated with the suction chamber 3a via.

In such a compressor, the suction chamber 3a
The inhalation pulsation that occurs in 1) can be smoothed by the same principle as in the embodiment of FIG. In each of the embodiments, the auxiliary discharge chamber 16 or the auxiliary suction chamber 18 is formed so as to include the central region of the cylinder block 1 in which the central shaft hole 1b is closed in the middle. If it extends to the end face of the auxiliary discharge chamber 16 around the central axis hole 1b.
Alternatively, the auxiliary suction chamber 18 is formed. Even such a configuration has an effect of smoothing the discharge pulsation or the suction pulsation.

Further, in the compressor in which the central shaft hole 1b extends to the end surface of the cylinder block 1 and the auxiliary discharge chamber 16 or the auxiliary suction chamber 18 is formed around it as described above, a chain wheel-shaped auxiliary discharge is formed. By causing the hollow portion corresponding to the valley portion of the chamber 16 or the auxiliary suction chamber 18 to function as a throttle, the interference action of the refrigerant gas occurs between the hollow portions corresponding to the ridges protruding between the bores, and further discharge pulsation occurs. Alternatively, a smoothing effect of inhalation 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 of FIG. 1 in that the discharge chamber 3 is provided in the inner peripheral region at the rear end of the cylinder block 1.
b, a cylinder head 3 having a suction chamber 3a formed in the outer peripheral region
Are connected via the valve plate 4. Further, a chain wheel-shaped auxiliary discharge chamber 21 is formed by piercing the cylinder block 1 in the inner peripheral region from the bore 1a.

The feature of this embodiment is that, in addition to having the inlet through hole 22 that connects 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. The outlet through hole 23 is provided. Specifically, the inlet through hole 22 is equivalent to the through hole 17 of the embodiment of FIG. 1 at any position in the circumferential direction with the axial center as the base point, and the valve plate 4 and the intake valve 1 are provided.
3 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 auxiliary 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, and the discharge chamber 3
It is communicated with a discharge port 25 formed in the end surface of the cylinder head 3 via a discharge passage 24 made of a pipe material extending in b. The discharge passage 24 may be formed by forming the cylinder head 3 in a concave shape toward the valve plate 4 side.

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

In particular, in the present embodiment, even when the indirect component caused by the shape of the discharge chamber 3b and the natural frequency of the equipment of the vehicle match, the component of the specific band in the sub-discharge chamber 21 is reduced. Therefore, it is possible to prevent a phenomenon that an abnormal noise is generated due to resonance with the equipment. Also, each bore 1a
Since the discharge hole 4b and the discharge passage 24 are separated by the auxiliary discharge chamber 16, there is no room for transmitting the direct component of the discharge pulsation to the pipe.

Therefore, this embodiment is more effective in reducing vibration and noise than the embodiment of FIG. Note that FIG.
The embodiment can also be applied to a compressor as shown in FIG. 5, that is, a compressor in which the positions of the discharge chamber and the suction chamber are exchanged, and the suction chamber is formed in the central region of the cylinder block and the discharge chamber is formed in the outer peripheral region. it can. In the configuration in this case, the suction chamber and the sub-suction chamber are communicated with each other through the outlet passage formed in the valve plate 4 and the suction valve 13, and the similarly formed inlet passage is communicated with the suction passage. With such an embodiment as well, like the discharge pulsation, it is possible to prevent the direct component of the suction pulsation and reduce the indirect component.

Also, in the embodiment of the compressor in which the positions of the discharge chamber and the suction chamber are exchanged, the outlet through hole is not limited to one like the through hole 17, and a plurality of them can be scattered. Is.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing the entire structure of a compressor according to an 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 the discharge chamber and the sub-discharge chamber when the discharge pulsation is smoothed according to 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 structure of a compressor according to another embodiment of the present invention.

FIG. 6 is a cross-sectional view showing the entire structure 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
... auxiliary suction chamber, 19 ... through hole, 22 ... inlet through hole, 23 ... outlet through hole, 24 ... discharge port.

Claims (5)

[Claims] 1. A cylinder block having a plurality of bores arranged 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 a compressor having a chamber formed therein, a sub-discharge chamber is provided in the cylinder block in an inner peripheral region of a plurality of bores, and the sub-discharge chamber is discharged through at least one through hole penetrating the valve plate. A reciprocating compressor characterized by being able to communicate with the room. 2. A cylinder block having a plurality of bores arranged 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 a compressor having a chamber formed therein, a sub-discharge chamber is provided in the cylinder block in an inner peripheral region of a plurality of bores, and the sub-discharge chamber is provided with at least one inlet through hole penetrating the valve plate. A reciprocating compressor characterized in that an outlet through hole penetrating the valve plate is connected to a discharge passage so as to communicate with the discharge chamber and to communicate with the auxiliary discharge chamber. 3. A cylinder block having a plurality of bores arranged 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 a compressor having a chamber formed therein, an auxiliary suction chamber is provided in the cylinder block in an inner peripheral region of a plurality of bores, and the auxiliary suction chamber is sucked through at least one through hole penetrating a valve plate. A reciprocating compressor characterized by being able to communicate with the room. 4. A cylinder block having a plurality of bores arranged 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 a compressor having a chamber formed therein, a sub suction chamber is provided in the cylinder block in an inner peripheral region of a plurality of bores, and the sub suction chamber is provided with at least one outlet through hole penetrating the valve plate. A reciprocating compressor characterized in that an inlet through hole penetrating the valve plate is connected to a suction passage so as to communicate with the suction chamber and communicate with the auxiliary suction chamber. 5. The reciprocating compressor according to claim 1, wherein the auxiliary discharge chamber or the auxiliary suction chamber is formed in a chain wheel shape so as to extend between the bores.