JPH09222078A - Reciprocation type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a reciprocation type compressor to reduce the generation of noise and vibration through reduction of the rotation n-th component of a torque fluctuation corresponding to the number of cylinders. SOLUTION: Cylinder bores 33-1-33-5 facing a pair of cylinder blocks and a double end piston is contained in the cylinder bores 33-1-33-5 to partition a compression chamber. In the gasket 28 and the suction valve forming plate 29 of the gasket 28 of a valve constituting body 24, by changing the shapes of through-holes 28a-1-28a-5 and 29a-1-29a-5 corresponding to the cylinder bores 33-1-33-5, the dead volume of each compression chamber is varied, the dead volumes of the compression chambers on both sides of the double end piston are set to the same as each other.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating compressor used in, for example, a vehicle air conditioner.

[0002]

2. Description of the Related Art In a reciprocating compressor of this type, a drive shaft is supported inside a housing and a crank chamber is formed. A plurality of cylinder bores are arranged in parallel to each other to surround the drive shaft in a cylinder block constituting a part of the housing. A piston is reciprocally housed in the cylinder bore to define a compression chamber. A swash plate is integrally rotatably mounted on the drive shaft, and the piston is reciprocated in association with the rotation of the swash plate to compress the refrigerant gas in the compression chamber.

During this compression operation, a compression reaction force acts on each of the pistons in accordance with the compression operation. This compression reaction force acts on the drive shaft via the swash plate, causing torque fluctuations. This torque fluctuation becomes an exciting force of torsional vibration of the drive shaft-clutch system. Here, when a fast Fourier transform (FFT) analysis is performed on the sum of the torque fluctuations, in other words, the sum of the compression reaction forces generated in the respective compression chambers, a wide range of frequency components from the 0th order to a considerably higher order is obtained. Of these frequency components, the main component is the n-th rotation component corresponding to the number of cylinders n. If the frequency of the rotation n-order component and the like is close to the natural frequency of the compressor and the auxiliary equipment connected thereto, noise due to the resonance phenomenon occurs, and the noise level in the passenger compartment is reduced. Was causing it to rise.

In order to solve such a problem, for example, Japanese Unexamined Utility Model Publication No. 1-160180 discloses that in a swinging swash plate type variable displacement compressor, when the arrangement of the cylinder bores is unequal due to the structure, a part of the variable displacement compressor is required. A configuration in which the dead volume of the compression chamber in the cylinder bore is changed is disclosed. Note that the dead volume is the volume of the compression chamber when the piston reaches the top dead center. In this reciprocating compressor, the dead volume is formed by cutting off the surface of the piston by a predetermined length. In the compression chamber in which the dead volume has been expanded, the transition curve between the volume and the pressure is changed with the expansion of the dead volume. Then, the compression reaction force generated in the compression chamber is reduced, and the sum of the compression reaction forces acting on the swinging swash plate is always equal, so that the generation of torsional vibration and noise is reduced.

[0005]

However, the above publication only discloses changing the dead volume of some of the cylinder bores in order to reduce the torsional vibration of the compressor. That is, there is no disclosure or suggestion of the regularity for taking measures against the torque fluctuation of the drive shaft. For this reason, there has been a problem that the torque fluctuation cannot be sufficiently reduced, and the generation of noise and vibration may not be sufficiently suppressed.

SUMMARY OF THE INVENTION An object of the present invention is to provide a reciprocating compressor in which the excitation force of torsional vibration is reduced, the rotational nth order component of torque fluctuation corresponding to the number of cylinders n is reduced, and noise and vibration are less generated. Is to do.

[0007]

In order to achieve the above object, in the invention of a reciprocating compressor according to claim 1, a drive shaft is supported inside a housing, and a piston can reciprocate inside a cylinder bore. To form a compression chamber, and a cam plate is integrally rotatably attached to the drive shaft, and the piston is reciprocated in association with the rotation of the cam plate to compress the refrigerant gas. In the reciprocating compressor described above, the valve assembly opposed to the cylinder block is formed of a gasket, a suction valve forming plate, a valve plate and a discharge valve forming plate, and each compression chamber has a predetermined dead volume. And the dead volumes are set to be changeable by the valve structure.

According to a second aspect of the present invention, in the reciprocating compressor according to the first aspect, the dead volume in each compression chamber changes the shapes of the gasket of the valve assembly and the intake valve forming plate. It has been changed by.

According to a third aspect of the present invention, in the reciprocating compressor according to the first or second aspect, the dead volume in each compression chamber is formed so as to increase in order along the rotational direction of the drive shaft. It is a thing.

[0010] According to the invention described in claim 4, claims 1 to 3 are provided.
In the reciprocating compressor according to any one of 1, the cylinder bores are formed to face each other in the front-rear direction, the piston is configured in a double-headed type, and a predetermined dead volume is formed in each compression chamber on both front and rear sides. is there.

According to a fifth aspect of the invention, in the reciprocating compressor according to the fourth aspect, the arrangement of the dead volumes of the front compression chambers and the sizes of the dead volumes of the rear compression chambers are large and small. Are arranged so that they are the same in the rotational direction of the drive shaft.

According to a sixth aspect of the present invention, in the reciprocating compressor according to the fourth or fifth aspect, the dead volume on the front side and the dead volume on the rear side have the same size for one piston. It was formed.

Therefore, in the reciprocating compressor configured as described above, the value of the dead volume (the volume of the compression chamber when the piston reaches the top dead center) is changed by each compression chamber (the same dead volume). The values of these dead volumes are set within the range of at least two types and n types or less (n is the number of compression chambers). For this reason, the transition curve of the volume and the pressure in each compression chamber is changed, and the torque fluctuation based on the compression reaction force generated in each compression chamber becomes different. Then, the n-th rotational component corresponding to the number of cylinders n obtained by the fast Fourier transform analysis of the sum of the torque fluctuations is reduced as compared with the case where the dead volume of each compression chamber is not changed.

Further, in the double-headed piston type compressor constructed as described above, in addition to the above-mentioned change of dead volume, for the same double-headed piston, the dead volume on the front side and the dead volume on the rear side are the same. It is formed to have the same size as the dead volume. The phase of the compression reaction force in this double-headed piston type compressor has a difference of 180 ° between the total sum on the front side and the total sum on the rear side. Here, the rotational n-th order component corresponding to the number of cylinders n of the torque fluctuation, which is the exciting force of the torsional vibration, becomes an even-order component in the double-headed piston type compressor. This even-order component is such that its phase repeats the same displacement an even number of times within a time corresponding to one rotation of the drive shaft. Therefore, the rotation n
The sum of the next component on the front side and the sum of the rear components on the rear side are superposed in phase with each other.

However, by changing the dead volume as described above, the total of the n-th order component of the rotation on the front side and the total of the rear side are reduced. And
The rotation n-order component of the entire compressor, on which the sum of the front side and the sum of the rear side are superimposed, is also reduced. Moreover, the rotation n
Even if the / 2nd-order component becomes an odd-order component, the odd-order component repeats the same displacement an odd number of times within a time corresponding to one rotation of the drive shaft, and the waveforms of the front and rear sides are mutually different. The state is reversed. For this reason, the rotational n / 2-order component cancels each other on the front side and the rear side of the same piston and disappears.

Further, in the reciprocating compressor constructed as described above, the dead volume in each compression chamber is changed by changing the shapes of the gasket and the suction valve forming plate of the valve assembly. Normally, the gasket and suction valve forming plate are molded into a predetermined shape by pressing, so they can be easily processed even if their shapes are changed, and the dead volume value of each compression chamber is highly accurate. Can be changed to

Moreover, the change of the dead volume is made in the valve structure. Therefore, the torsional vibration system of the compressor can be changed only by changing the valve structure. Then, it is possible to easily cope with a resonance frequency that differs depending on the type of the mounted vehicle without largely changing the overall configuration of the compressor.

[0018]

BEST MODE FOR CARRYING OUT THE INVENTION

(First Embodiment) A first embodiment of the present invention will be described below with reference to FIGS.

As shown in FIG. 1, the cylinder block 21 on the front side and the cylinder block 22 on the rear side are joined at the central portion. A front housing 25 is joined to the front end surface of the cylinder block 21 via a valve assembly 23, and a rear housing 26 is joined to the rear end surface of the cylinder block 22 via a valve assembly 24. There is. The cylinder block 2
1, 22, front housing 25, rear housing 2
6 and the valve components 23 and 24 are fastened and fixed to each other by a plurality of through bolts 27, which form a housing of the compressor.

As shown in FIGS. 1 to 8, each of the valve components 23 and 24 has a gasket 28 and a suction valve forming plate 29.
, A valve plate 30, a discharge valve forming plate 31, and a gasket 32 also serving as a retainer plate. Five intake ports 30a and five discharge ports 30b are formed on the valve plate 30 at predetermined intervals. The gasket 28 includes each suction port 30a and each discharge port 30a of the valve plate 30.
b, five through holes 28a-1, 28a-2,
28a-3, 28a-4 and 28a-5 are formed.

The suction valve forming plate 29 is provided with a gasket 2
The eight through holes 29a-1, 29a-2, 29a-3, 29a-4, 29 correspond to the eight through holes 28a-1 to 28a-5.
a-5 are formed. In each of the through holes 29a-1 to 29a-5, the suction valves 29b-1, 29b-2, 29b-3, 29 are opened and closed so as to open and close each suction port 30a of the valve plate 30.
b-4 and 29b-5 are formed to protrude.

The discharge valve forming plate 31 includes five discharge valves 31a-1, 31a-2, 31a-3, 31a-4, 31 so as to open and close each discharge port 30b of the valve plate 30.
a-5 are formed. The gasket 32, which also serves as a retainer plate, is formed with five retainers 32a so as to regulate the maximum opening of each of the discharge valves 31a-1 to 31a-5.

As shown in FIGS. 1 to 4 and 8, the cylinder blocks 21 and 22 include a plurality of cylinder bores 3.
3-1, 33-2, 33-3, 33-4, 33-5 are formed so as to be parallel to each other. Each cylinder bore 33-1
A double-headed piston 34 is reciprocally housed inside the members 33-5. Between the two ends of these pistons 34 and the valve components 23, 24, each cylinder bore 33-1
A pair of front and rear compression chambers 35 and 36 are formed in each of ~ 33-5. The compressor of this embodiment is a 10-cylinder type reciprocating compressor including five double-headed pistons 34.

An annular partition wall 37 is formed in the front housing 25 and the rear housing 26, and the partition walls 37 define suction chambers 38, 39 on the outer peripheral sides of the housings 25, 26, respectively. Discharge chambers 40 and 41 are formed on the center side. Each of the suction chambers 38, 39 is connected to the compression chamber 3 via a suction port 30a formed in the valve plate 30 of the valve component 23, 24.
It is connected to 5,36. In addition, each discharge chamber 40, 41
Are communicated with the compression chambers 35 and 36 via discharge ports 30b formed in the valve plates 30 of the valve components 23 and 24.

A crank chamber 42 is formed in the center of each of the cylinder blocks 21 and 22. A drive shaft 43 is rotatably supported in the shaft holes 21a and 22a of both cylinder blocks 21 and 22 via a radial bearing 44. The drive shaft 43 is rotated by an external drive source such as a vehicle engine via a clutch (not shown).

At the intermediate outer peripheral portion of the drive shaft 43,
A swash plate 45 as a cam plate is fitted and fixed. The double-headed piston 34 is anchored to the swash plate 45 via a shoe 46, and the double-headed piston 34 is reciprocated in the cylinder bores 33-1 to 33-5 by the rotation of the swash plate 45. In addition,
The boss portion 45a of the swash plate 45 is provided with a thrust bearing 47,
Cylinder blocks 21, 22 forming the crank chamber 42
It is supported on the front and rear side walls.

The crank chamber 42 is communicated with the suction chambers 38, 39 via suction passages 48 formed in the cylinder blocks 21, 22 and the valve components 23, 24.
The crank chamber 42 is connected to an external refrigerant circuit via a suction flange (not shown) formed in the cylinder blocks 21 and 22. Further, the discharge chambers 40, 41 are connected to an external refrigerant circuit via a discharge passage 49 formed in the valve components 23, 24 and the cylinder blocks 21, 22 and a discharge flange (not shown) formed in the cylinder blocks 21, 22. ing.

As shown in FIGS. 1 and 3 to 6, the cylinder bores 33-1 to 33-5 have the same inner diameter. Further, in each of the valve components 23 and 24, the gasket 28 and the suction valve forming plate 29 have their through holes 28a-1 to 28a-5 and 29a-1 to 29a-5 changed in shape so that their openings are improved. The amount is different. Moreover, each through hole 28a-1 to 28a-5, 29a-1 to 2
The shape of 9a-5 is formed so that the front valve structure 23 and the rear valve structure 24 have the same shape with the double-headed piston 34 interposed therebetween.

Therefore, when each piston 34 reaches the top dead center position, each cylinder bore 33-1 to 33-5, between the head end surface of the piston 34 and the valve plate 30.
The volumes of the spaces formed by the through holes 28a-1 to 28a-5 of the gasket 28 and the through holes 29a-1 to 29a-5 of the suction valve forming plate 29 are different. As a result, the dead volumes in the compression chambers 35 and 36 are set to different values. The dead volume is the volume of the compression chambers 35 and 36 when the piston 34 reaches the top dead center position.

Here, the dead volume of each compression chamber 36 on the rear side will be described in detail. 3, FIG. 5, FIG.
As shown in FIGS. 9 and 10, regarding the through holes 28a-1 and 29a-1 corresponding to the cylinder bore 33-1, the opening amount is minimum and the dead volume of the compression chamber 36 is minimum. . The through holes 28a-2 and 29a-2 corresponding to the cylinder bore 33-2, the through holes 28a-4 and 29a-4 corresponding to the cylinder bore 33-4, and the through holes 28a-3 and 29a corresponding to the cylinder bore 33-3. The opening amount increases in the order of −3, and the dead volume of the compression chambers 36 is enlarged. Also, the through hole 28 corresponding to the cylinder bore 33-5.
The a-5 and 29a-5 are formed to have the same opening amounts as the through holes 28a-3 and 29a-3 corresponding to the cylinder bore 33-3, and the dead volume of the compression chamber 36 is maximized. There is.

Further, the front-side valve assembly 23 and the rear-side valve assembly 24 are sandwiched by the double-headed pistons 34.
And through holes 28a-1 to 28a-5, 29a-1 to 2
9a-5 are formed to have the same shape. Therefore, for one double-headed piston 34, the dead volume of the front compression chamber 35 and the dead volume of the rear compression chamber 36 are the same. In other words, the compression chamber 35 in the front side cylinder bore 33-1 and the rear side cylinder bore 3 that face each other in the axial direction of the drive shaft 43 with the double-headed piston 34 interposed therebetween.
The compression chamber 36 in 3-1 is set to the same dead volume.

Similarly, the cylinder bores 33-2, 33-3, 3
Also for 3-4 and 33-5, the dead volumes of the compression chamber 35 and the compression chamber 36 are the same on the front side and the rear side, respectively. Therefore, the size of the dead volume of each compression chamber 35 on the front side and the size of the dead volume of each compression chamber 36 on the rear side are formed to be the same in the rotation direction of the drive shaft 43. I have. As described above, in the compressor of this embodiment, four types of dead volumes are formed.

Next, the operation of the reciprocating compressor having the above structure will be described. When the drive shaft 43 is rotated by an external drive source such as a vehicle engine, the swash plate 45 in the crank chamber 42 is rotated, and the plurality of double-headed pistons 34 are connected to the cylinder bores 33-1 to 33 through the shoes 46.
-Move back and forth within -5. Due to the movement of the double-headed piston 34, the refrigerant gas introduced from the external refrigerant circuit (not shown) into the crank chamber 42 via the intake flange is introduced into the intake chambers 38, 39 from the crank chamber 42 via the intake passage 48. In the re-expansion / suction stroke in which the double-headed piston 34 moves from the top dead center to the bottom dead center, the pressure in the compression chambers 35, 36 decreases, the suction valves 29b-1 to 29b-5 are opened, and the suction chamber 38, The refrigerant gas in 39 is sucked into the compression chambers 35, 36 through the suction port 30a.

Next, in the compression / discharge stroke in which the double-headed piston 34 moves from the bottom dead center to the top dead center, the compression chambers 35, 36 are
The refrigerant gas inside is compressed. When the refrigerant gas reaches a predetermined pressure, the high pressure compressed refrigerant gas is discharged into the discharge valve 31a-1.
~ 31a-5 are pushed away and discharged into the discharge chambers 40, 41 through the discharge port 30b. Furthermore, the discharge chambers 40, 4
The compressed refrigerant gas in 1 is supplied to a condenser, an expansion valve, and an evaporator, which form an external refrigerant circuit, through a discharge passage 49 and a discharge flange (not shown), and is used for air conditioning in the vehicle compartment.

As shown in FIG. 14, in the 10-cylinder double-headed piston type compressor, the phase of the compression reaction force in each compression chamber is 1 for the sum of the front side and the sum of the rear side.
It will be shifted by 80 degrees. In addition, the rotational tenth-order component as the rotational nth-order component obtained by the fast Fourier transform analysis of the sum of the compression reaction forces of the compression chambers is 1
The waveform has a waveform in which the same displacement is repeated 10 times, that is, an even number of times, during the rotation time. Here, when the dead volumes of the compression chambers are the same, the rotational tenth-order component originating from each compression chamber has a regular waveform, and the phase of the sum on the front side and the phase of the sum on the rear side are equal to each other. And are an exact match. Then, the rotational tenth-order component of the torque fluctuation derived from the compression reaction force of each compression chamber is completely superimposed and becomes the main component of the exciting force of the torsional vibration between the drive shaft 43 and the clutch (not shown).

In this case, the rotational fifth-order component as the rotational n / 2nd-order component is such that the same displacement is repeated five times, that is, an odd number of times, during one rotation of the drive shaft 43. The fifth order component of rotation has a 180 ° phase shift between the sum on the front side and the sum on the rear side, and cancels each other.

Here, when the dead volume is made different between the front side and the rear side of the same double-headed piston 34 in order to reduce the rotational tenth order component, as shown in FIG. The components are reduced by causing a phase shift between the total sum on the front side and the total sum on the rear side. However,
The rotational fifth-order component also has a different phase shift between the front side and the rear side, similarly to the rotational tenth-order component, and a new overlapping portion is generated. For this reason, the rotation fifth-order component of the torque fluctuation may become a new noise generation factor.

On the other hand, in the compressor of this embodiment, the dead volumes of the compression chambers 35 and 36 on the front side and the rear side are changed to four types. As the dead volumes of the compression chambers 35 and 36 are changed, the curves of the changes in the volumes and pressures of the compression chambers 35 and 36 become different. That is, FIG.
As shown in FIG. 1, there is a difference in the timing of the pressure change in the compression chambers 35 and 36 between the re-expansion stroke and the compression stroke between the small dead volume and the large dead volume. Also, there is a difference in the pressure during overcompression in the final stage of the compression stroke.

As a result, as shown in FIG. 12, between the one with a small dead volume and the one with a large dead volume, the peak position of the torque is shown in the transition curve of the compression torque per compression chamber 35, 36. There is a difference. Then, the compression chambers 3 with the dead volumes changed
The transition curve of the compression torque is different for each of 5 and 36. Therefore, in the total sum of the compression reaction forces, the overlapping portion of the phase of the torque fluctuation is reduced, and the rotational tenth-order component of the torque fluctuation corresponding to the number of cylinders obtained by the fast Fourier transform analysis is reduced.

Further, the dead volumes of the compression chamber 35 on the front side and the compression chamber 36 on the rear side of one double-headed piston 34 are formed to be the same. For this reason, the fifth-order rotational component cancels each other out while maintaining a 180 ° phase shift between the front-side total and the rear-side total.

According to the embodiment configured as described above, the following excellent effects are exhibited. (A) On the front side and the rear side, the dead volume of each compression chamber 35, 36 is changed to four types. As a result, in the 10-cylinder type double-headed piston type compressor, the 10th-order rotational component, which is the main component of the torque fluctuation that becomes the exciting force of the torsional vibration, is reduced. Accordingly, due to the torsional vibration, the generation of noise due to the resonance phenomenon of the compressor and the auxiliary equipment connected thereto is reduced, and the noise level in the vehicle compartment is reduced.

(B) The front side compression chamber 35 and the rear side compression chamber 36 of one double-headed piston 34 are formed to have the same dead volume. For this reason, the fifth order component of rotation disappears because the total sum on the front side and the total sum on the rear side cancel each other. Therefore, in combination with the effect of the above item (a), the rotation of torque fluctuation 10
It is possible to suppress the generation of the fifth-order rotation component while reducing the second-order component.

(C) In the compressor of this embodiment, the through holes 28a-1 to 28a-5, 29a-1 to 29 on the gasket 28 and the suction valve forming plate 29 in both valve components 23 and 24 are provided.
By changing the shape of a-5, each compression chamber 35, 3
The dead volume value in 6 has been changed. Normally, the gasket 28 and the suction valve forming plate 29 are formed by press working, and therefore the through holes 28 formed therein are formed.
Even if the shapes of a-1 to 28a-5 and 29a-1 to 29a-5 change, the processing can be easily performed. Further, by appropriately changing the shapes of the through holes 28a-1 to 28a-5 and 29a-1 to 29a-5, the values of the dead volumes of the compression chambers 35 and 36 can be changed with high accuracy. it can. Moreover, the torsional vibration system of the compressor can be changed only by changing the gasket 28 and the suction valve forming plate 29 without largely changing the overall structure of the compressor. Therefore, it is possible to easily cope with the resonance frequency that differs depending on the vehicle type of the mounted vehicle.

(Second Embodiment) The second embodiment of the present invention will be described below.
An embodiment will be described based on FIG. In the second embodiment, in the 10-cylinder double-headed piston type compressor, the compression chambers 35 in the cylinder bores 33-1 to 33-5,
The dead volume of 36 is formed so as to increase in order along the rotation direction of the drive shaft 43. In addition, a compression chamber 35 in the front cylinder bores 33-1 to 33-5, which faces each other via one double-headed piston 34,
The dead volume is set to be the same as that of the compression chambers 36 in the rear cylinder bores 33-1 to 33-5.

That is, as shown in FIG. 15, in both valve components 23 and 24, the gasket 28 corresponding to the cylinder bore 33-1 and the through holes 28a-1 and 2 of the intake valve forming body 29 are formed.
9a-1 is formed so that the opening amount is minimized, and the dead volumes of the compression chambers 35 and 36 are minimized. Then, along the rotation direction of the drive shaft 43, the through holes 28a corresponding to the cylinder bores 33-2 to 33-5.
-2, 29a-2, through hole 28a-3, 29a-3, through hole 28a-
In the order of 4, 29a-4 and through holes 28a-5, 29a-5, the opening amounts thereof are gradually increased, and the dead volumes of the compression chambers 35, 36 are enlarged.

Even in the case of such a configuration, it is possible to suppress the generation of the rotational fifth-order component while reducing the rotational tenth-order component, in substantially the same manner as in the first embodiment. (Third Embodiment) The third embodiment of the present invention will be described below.
This will be described with reference to FIG.

In the third embodiment, each cylinder bore 3
Corresponding to No. 3, a recess 51 is formed in the valve plate 30 of both valve assemblies 23, 24. Then, the opening area or depth of these recesses 51 is changed and, as shown in the first and second embodiments, the gasket 2
8 and through holes 28a-1 to 28a-5 on the suction valve forming body 29,
The opening amounts of 29a-1 to 29a-5 are changed. As a result, the compression chambers 35 in the cylinder bores 33-1 to 33-5,
The 36 dead volumes are set to be different.

Even in the case of such a configuration, it is possible to suppress the generation of the rotational fifth-order component while reducing the rotational tenth-order component in the same manner as in the first embodiment. Further, in the third embodiment, the through holes 28a-1 to 28a-5, 29a-1 to 2 on the gasket 28 and the suction valve forming body 29 are formed.
The valve plate 30 as well as the change in the opening amount of 9a-5
The dead volume of the compression chambers 35 and 36 can be changed by changing the opening area or depth of the upper recess 51. Therefore, it is possible to secure a large difference between the minimum dead volume value and the maximum dead volume value.

The present invention can be modified and embodied as follows. (1) The present invention is embodied in a double-headed piston compressor having the number of cylinders other than those described in the above embodiment, for example, 6, 8 or 12 cylinders.

(2) The types of dead volumes of the compression chambers 35 and 36 on the front side and the rear side, respectively, are other than those described in the above embodiment, for example, 2 or 3 types.

(3) Two or more types of dead volumes should be changed in only one of the front compression chambers 35 or the rear compression chambers 36. (4) Embodying the present invention in a single-head piston compressor.

Even with the above configuration, it is possible to reduce the rotational nth order component corresponding to the number of cylinders n. (5) Embodying the present invention in a wave cam plate type reciprocating compressor.

[0053]

As described above in detail, the present invention has the following excellent effects. At least two kinds of predetermined dead volumes are set in each compression chamber. Moreover, the dead volume of each compression chamber is set to be changeable by the valve structure.

Therefore, the rotational nth order component of the torque fluctuation corresponding to the number of cylinders n is reduced, and the exciting force of the torsional vibration of the drive shaft-clutch system is suppressed. Then, in the compressor and the auxiliary equipment connected thereto, the resonance phenomenon excited by the torsional vibration is reduced, and the noise level in the vehicle compartment can be reduced.

Further, in the double-headed piston type compressor,
The dead volume on the front side and the dead volume on the rear side with respect to one piston are configured to have the same size. Therefore, when the rotation n / 2-order component becomes an odd-order component, the front side and the rear side of one piston cancel each other and disappear. Therefore, in combination with the effect of the invention described above, it is possible to suppress the generation of the rotation n / 2-order component while reducing the rotation n-order component corresponding to the number of cylinders n. Then, the occurrence of a new vibration generation factor due to the countermeasure for the rotation n-order component is prevented.

Further, in this compressor, the dead volume in each compression chamber is changed by changing the shapes of the gasket of the valve structure and the suction valve forming plate. Therefore, the value of the dead volume of each compression chamber can be changed with high accuracy by a simple configuration in which the shapes of the gasket and the intake valve forming plate are changed. Also,
The torsional vibration system of the compressor can be changed only by changing the valve structure, and it is possible to easily cope with different resonance systems for each vehicle type of the mounted vehicle.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a compressor of a first embodiment.

FIG. 2 is a partial cross-sectional view showing a part of the compressor of FIG. 1 in an enlarged manner.

FIG. 3 is an exploded perspective view of a rear valve assembly and its related configuration.

FIG. 4 is a sectional view taken along line 4-4 in FIG. 2;

FIG. 5 is a sectional view taken along line 5-5 in FIG. 2;

6 is a sectional view taken along line 6-6 of FIG.

7 is a sectional view taken along line 7-7 of FIG.

8 is a sectional view taken along line 8-8 of FIG.

9 is a partial cross-sectional view taken along line 9-9 of FIG.

10 is a partial cross-sectional view taken along line 10-10 of FIG.

FIG. 11 is an explanatory diagram showing the relationship between the shaft rotation angle and the bore pressure.

FIG. 12 is an explanatory diagram showing a relationship between a shaft rotation angle and a compression torque per compression chamber.

FIG. 13 is an explanatory diagram showing a reduction of a rotation tenth-order component and a change of a rotation fifth-order component.

14A is an explanatory diagram regarding a superposition phenomenon of a sum total on a front side and a sum total on a rear side regarding a rotational fifth-order component and FIG. 14B illustrates a rotational tenth-order component.

FIG. 15 is a cross-sectional view showing the main parts of the compressor of the second embodiment.

FIG. 16 is a partial cross-sectional view showing an enlarged main part of the compressor of the third embodiment.

[Explanation of symbols]

21, 22 ... Cylinder block forming a part of housing, 23, 24 ... Valve structure, 25 ... Front housing forming a part of housing, 26 ... Rear housing forming a part of housing, 28 ... Gasket, 29
... Suction valve forming plate, 30 ... Valve plate, 31 ... Discharge valve forming plate, 32 ... Gasket that also serves as retainer plate
3-1 to 33-5 ... Cylinder bore, 34 ... Double-headed piston, 3
5, 36 ... Compression chamber, 42 ... Crank chamber, 43 ... Drive shaft, 45 ... Swash plate as cam plate.

Front Page Continuation (72) Inventor Tetsuyuki Shintoku 2-1, Toyota-cho, Kariya City, Aichi Stock Company Toyota Industries Corp.

Claims (6)

[Claims] 1. A drive shaft is supported inside a housing to form a crank chamber, and a plurality of cylinder bores are arranged in a cylinder block forming a part of the housing so as to surround the drive shaft. A piston is reciprocally housed in the compression chamber to define a compression chamber, a cam plate is integrally rotatably mounted on the drive shaft, and the piston is reciprocally moved in association with the rotation of the cam plate to cool the refrigerant. In a reciprocating compressor that compresses gas, a valve assembly disposed opposite to the cylinder block is formed of a gasket, a suction valve forming plate, a valve plate, and a discharge valve forming plate, and each compression chamber Each have a predetermined dead volume, and these dead volumes are set so as to be changeable by a valve structure body. Compressor. 2. The reciprocating compression according to claim 1, wherein the dead volume in each compression chamber is changed by changing the shapes of the gasket of the valve structure and the suction valve forming plate. Machine. 3. The reciprocating compressor according to claim 1, wherein a dead volume in each of the compression chambers is formed so as to increase in order along the rotation direction of the drive shaft. 4. The cylinder bores are formed so as to face each other in the front-rear direction, the piston is configured as a double-headed type, and a predetermined dead volume is formed in each of the compression chambers on the front and rear sides. The reciprocating compressor according to any one of 3 above. 5. The arrangement is such that the arrangement of the dead volumes of the front compression chambers and the arrangement of the dead volumes of the rear compression chambers are the same in the rotational direction of the drive shaft. The reciprocating compressor according to claim 4. 6. The reciprocating compressor according to claim 4, wherein a front dead volume and a rear dead volume are formed in the same size for one double-headed piston. .