JP3489339B2 - Muffler structure of 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 compressor applied to, for example, a vehicle air conditioning system, and more particularly to a muffler structure of the compressor.

[0002]

2. Description of the Related Art Conventionally, there has been a compressor provided with an expansion type muffler in order to reduce vibration and noise generated by the operation of the compressor. The muffler space forming the muffler is formed by forming a recess on the outside of the housing forming body forming the housing, and sealing the recess by a lid separate from the housing forming body. The muffler expands the passage cross-section area of the intake gas or the discharge gas by the muffler space and reduces the passage cross-section area again, so that the pressure pulsation of the suction gas or the discharge gas is reflected and interferes in the muffler space. And decay. Since the pressure pulsation of the suction gas or the discharge gas is attenuated, vibration and noise accompanying the operation of the compressor are reduced.

[0003]

However, the above-mentioned conventional technique has the following problems. (1) In order to effectively attenuate the pressure pulsation of the suction gas or the discharge gas with the expansion type muffler, a muffler space having a sufficient capacity is generally required, and the muffler is enlarged. Larger capacity of the muffler leads to larger compressor,
For example, in a compressor for a vehicle air conditioning system installed in a small engine room, this is a problem that should be avoided as much as possible.

(2) In order to form the muffler space, a lid member separate from the housing structure is required, and the number of parts constituting the compressor increases, and as the number of parts increases, its assembling process The number of compressors has increased and the manufacturing cost of the compressor has increased.

The present invention has been made by paying attention to the problems existing in the above-mentioned prior art, and the object thereof is to construct a muffler space with a small number of parts and also to increase the capacity of the intake gas. Alternatively, it is to provide a muffler structure of a compressor capable of sufficiently attenuating the pressure pulsation of discharge gas.

[0006]

In order to achieve the above object, in the invention of claim 1, a muffler forming space is formed outside the housing structure, and an opening of the muffler forming space is formed by joining the housing structure bodies to each other. a muffler structure hoax hula formation <br/> space is configured to seal. The muffler forming sky
In between by expanding the housing structure inward.
And the resonance space communicated via the neck formed by
The resonance muffler space and the passage space are composed of a hula space.
Are arranged side by side along the circumferential direction of the housing structure.
There is .

[0007]

According to a second aspect of the present invention, the compression mechanism includes a cylinder bore formed in a cylinder block, which is a housing structure, and a double-headed piston housed in the cylinder bore and reciprocated. The discharge gas discharged from the compression chamber formed by being surrounded by the piston end surface and the cylinder bore, and the discharge gas discharged from the compression chamber formed by being surrounded by the other piston end surface and the cylinder bore are the passage space. The inlet of the discharge gas from one compression chamber side and the inlet of the discharge gas from the other compression chamber side are arranged to face each other in the same passage space. The entrance is
Provided at the joint with the housing and the other
The mouth is provided at a joint with the rear housing .

(Operation) In the invention of claim 1 having the above structure, the muffler forming space is formed outside the housing constituent body, and the muffler forming space is sealed by joining the housing constituent bodies to each other, thereby causing resonance. A muffler space is constructed. Therefore,
In constructing the resonance muffler space, a member separate from the housing structure is not required, and the number of constituent parts can be reduced.

Then, a part of the suction gas or the discharge gas passing through the passage space enters and leaves the resonance muffler space through the neck, whereby the pressure pulsation component is resonated and the pressure of the suction gas or the discharge gas is resonated. Pulsations are dampened.

[0011] Then, the passage space is constructed by partitioning by cervical the muffler forming space are sealed at the same time sealing the resonance muffler space by joining of the housing component. Therefore, in forming the passage space, a member separate from the housing structure is not required, and the number of constituent parts can be reduced.

According to the second aspect of the present invention, the discharge gas discharged from one compression chamber and the discharge gas discharged from the other compression chamber merge in the passage space.
Here, the inlet of the discharge gas from one compression chamber side and the inlet of the discharge gas from the other compression chamber side face each other in the same passage space. Therefore, the two discharge gases collide with each other in the passage space to interfere with each other's pressure pulsation component, and the pressure pulsation of the discharge gas from the compressor is attenuated.

[0013]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment in which the present invention is embodied in a muffler structure of a double-headed piston type compressor will be described below.

As shown in FIG. 1, a pair of cylinder blocks 11A and 11B as a housing structure are joined to each other at opposite edges. Similarly, the front housing 12 as a housing structure has a front valve forming body 1 on the front end surface of the front cylinder block 11A.
It is joined via 3. Similarly, the rear housing 14 as a housing structure is joined to the rear end surface of the rear cylinder block 11B via the rear valve forming body 15.

A plurality of bolt insertion holes 16 are formed in the rear housing 14 from the front housing 12 through the front valve forming body 13, both cylinder blocks 11A and 11B, and the rear valve forming body 15. The plurality of through bolts 17 are inserted into the bolt insertion holes 16 from the front housing 12 side, and are screwed into the screw holes 16a formed in the rear housing 14 at the tips thereof. The front housing 12 and the rear housing 14 are fastened and fixed to the end surfaces of the corresponding cylinder blocks 11A and 11B by these through bolts 17.

The drive shaft 18 is the cylinder block 11 described above.
In the center of A, 11B and the front housing 12, a pair of front and rear radial bearings 19 are rotatably supported. The lip seal 20 is interposed between the outer periphery of the front end of the drive shaft 18 and the front housing 12.
The drive shaft 18 is operatively connected to an external drive source such as a vehicle engine via a clutch (not shown), and when the clutch is engaged, the drive force of the external drive source is transmitted to be rotationally driven.

As shown in FIG. 2, a plurality of cylinder bores 2
1 is formed so as to extend in parallel with the drive shaft 18 between both ends of each cylinder block 11A, 11B on the same circumference at predetermined intervals. A plurality of double-headed pistons 22 are reciprocally fitted and supported in the respective cylinder bores 21, and between both end faces and the valve forming bodies 13 and 15, the compression chambers 23 (front side) are provided in the respective cylinder bores 21. ), 24 (rear side) are formed in plural.

The crank chamber 25 is defined inside the middle of the cylinder blocks 11A and 11B. The swash plate 26 is fitted and fixed to the drive shaft 18 in the crank chamber 25, and the outer peripheral portion of the swash plate 26 is connected to the piston 2 via the shoe 27.
It is moored in the middle of 2. And the piston 22
Are reciprocated through the swash plate 26 by the rotation of the drive shaft 18. A pair of front and rear thrust bearings 28 are provided on the swash plate 26.
Is interposed between both end surfaces of the cylinder block 11 and the inner end surface of each cylinder block 11, and the swash plate 26 is interposed via the thrust bearing 28.
Are clamped and held between both cylinder blocks 11A and 11B. The crank chamber 25 is connected to an external refrigerant circuit (not shown) via the introduction passage 49 and the suction port 50 and constitutes a suction pressure region.

Front suction chamber 29 and rear suction chamber 3
0 is defined in the inner peripheral portions of the front housing 12 and the rear housing 14. The suction passage 31 is provided through both cylinder blocks 11A and 11B, and connects the front suction chamber 29 and the rear suction chamber 30 to the crank chamber 25, respectively. The front-side discharge chamber 32 and the rear-side discharge chamber 33 are formed in an annular shape on the outer peripheral portions of the front housing 12 and the rear housing 14.

A plurality of suction holes 34 are provided in the valve forming bodies 13 and 15 so as to correspond to the cylinder bores 21. The suction valve 35 is formed in each of the valve forming bodies 13 and 15 and opens and closes each suction hole 34. Then, the suction valve 35 is opened as the piston 22 moves from the top dead center position to the bottom dead center position, and the refrigerant gas is sucked into the compression chambers 23, 24 from both suction chambers 29, 30.

A plurality of discharge holes 36 are provided through the valve forming bodies 13 and 15 corresponding to the cylinder bores 21. The discharge valve 37 is formed in each of the valve forming bodies 13 and 15, and opens and closes each discharge hole 36. The discharge valve 37 is moved along with the movement of the piston 22 from the bottom dead center position to the top dead center position.
By this action, the refrigerant gas in each compression chamber 23, 24 is compressed to a predetermined pressure and discharged into both discharge chambers 32, 33. In addition, the opening degree of the discharge valve 37 is determined by the valve forming bodies 13, 1
5 are regulated by retainers 38 that are polymerized.

Next, the muffler structure of the double-headed piston type compressor having the above construction will be described. As shown in FIGS. 1 to 3, the front side bulging portion 41A is integrally formed outside the front side cylinder block 11A. Rear side bulge 4
1B is integrally formed on the outer side of the rear cylinder block 11B, and is continuous with the front bulging portion 41A in the joined state of both cylinder blocks 11A and 11B. The muffler forming space 42 is formed inside each of the bulging portions 41A and 41B, and is opened at the joint surface with the bulging portions 41B and 41A facing each other. And both cylinder blocks 11
The muffler forming spaces 42 are sealed by joining A and 11B (bulging parts 41B and 41A), and both muffler forming spaces 42 form an integrated space. The muffler forming space 42 extends in the circumferential direction along the outer wall surfaces 11a of the cylinder blocks 11A, 11B in order to obtain a predetermined volume, and the bulging portions 41A, 41 are preferably provided.
The degree of protrusion of B is reduced. Further, the muffler forming space 42 is formed so as to straddle both the bulging portions 41A and 41B to increase the volume of the muffler forming space 42.
This contributes to reducing the degree of protrusion of 1A and 41B.

As shown in FIGS. 2 and 3, the neck 43 is
The outer wall surface 11a (inner surface of the muffler forming space 42) of both cylinder blocks 11A and 11B is expanded toward the muffler forming space 42 side, and the discharge gas flowing in the direction crossing the muffler forming space 42 (the left-right direction in FIG. 2). It is configured by reducing the passage cross-sectional area at the same bulging portion. As shown by the mesh line in FIG. 3, the neck portion 43 is provided so as to cross the muffler forming space 42, and the muffler forming space 42 is formed by the neck portion 43 in the passage space 44 and the resonance muffler space 45. It is divided into and.

In the present embodiment, the outer wall surface 11a of the cylinder blocks 11A and 11B is bulged toward the muffler forming space 42 so that the bulging portion becomes thick, and the rear cylinder block 11B has the same wall thickness. The above-mentioned introduction passage 49 is provided through the portion.

The two discharge chambers 32 and 33 are connected to the cylinder blocks 11A and 11B from the valve forming bodies 13 and 15, respectively.
It is communicated with the passage space 44 through communication passages 46 and 47 which are respectively provided through the above. Double passage 4
6, 47, the entrance 46a, 47a to the passage space 44,
The passage spaces 44 are arranged so as to face each other. The discharge port 48 is formed on the outer surface of the rear side bulging portion 41B, and the passage space 44 is formed in the discharge port 48.
Through the external refrigerant circuit.

As described above, the muffler structure of this embodiment is
A so-called resonance type muffler is configured, and each discharge chamber 32, 3
The pressure pulsation of the discharge gas discharged from 3 to the external refrigerant circuit via the passage space 44 and the discharge port 48 is attenuated by the resonator including the neck portion 43 and the resonance muffler space 45.

Next, the operation of the double-headed piston type compressor having the above construction will be described. By connecting the clutch,
When a driving force is transmitted to the drive shaft 18 from an external drive source such as a vehicle engine, the piston 22 is interlocked with the rotation of the swash plate 26.
The reciprocating motion of is started. When the reciprocating motion of the piston 22 is started, in each compression chamber 23, 24, as the piston 22 reciprocates, the refrigerant gas is sucked from the suction chambers 29, 30 and compressed in the compression chambers 23, 24. , And the discharge chambers 32, 3
The discharge cycle to 3 is started.

The front and rear discharge chambers 3
The discharge gas discharged to the nozzles 2 and 33 is connected to the communication passage 4 respectively.
It flows into the passage space 44 via 6, 47. A part of the discharge gas that has flowed into the passage space 44 flows in and out of the resonance muffler space 45 via the neck portion 43 due to the pressure pulsation (periodic change in pressure). The pressure pulsation component resonates due to the inflow and outflow of the discharge gas, and the pressure pulsation of the discharge gas discharged through the discharge port 48 is absorbed and attenuated.
The frequency range of the pressure pulsation component to be damped has been investigated in advance by a test or the like, and the passing cross-sectional area or width of the neck 43, the volume of the resonance muffler space 45, etc. are set according to the frequency range. It

An inlet 46a from the front discharge chamber 32 to the passage space 44 and an inlet 47a from the rear discharge chamber 33 to the passage space 44 are opposed to each other. Therefore, the discharge gas flowing from the front discharge chamber 32 into the passage space 44 and the discharge gas flowing from the rear discharge chamber 33 collide with each other in the passage space 44. As a result, the pressure pulsation components interfere with each other, so that the pressure pulsation of the discharge gas discharged from the discharge port 48 toward the external refrigerant circuit is also attenuated.

The present embodiment having the above-mentioned structure has the following effects. (1) The bulging portions 41A and 41B are the cylinder block 11
It is integrally formed on the outside of A and 11B. Then, by forming the muffler forming space 42 inside the bulging portions 41A and 41B, respectively, the muffler forming space 42 is sealed by joining the cylinder blocks 11A and 11B to form the resonance muffler space 45. Therefore, to form the resonance muffler space 45, a member separate from the cylinder blocks 11A and 11B is not required, and the number of parts constituting the muffler structure can be reduced, the number of assembling steps can be reduced, and compression can be performed. This leads to lower machine costs.

Further, the muffler structure of this embodiment is a resonance type muffler which attenuates the pressure pulsation of the discharge gas by resonance. In the resonance muffler, it is important to set the passage cross-sectional area and width of the neck portion 43, the volume of the resonance muffler space 45, and the like to appropriate values in order to attenuate the pressure pulsation of the discharge gas.
Therefore, in order to sufficiently exert the damping effect of the pressure pulsation by the resonance type muffler, the capacity is not necessarily increased. Therefore, for example, the muffler structure can be made compact and the compressor can be made compact as compared with an expansion type muffler which focuses on expanding the discharge gas.

(2) The passage space 44 is the muffler forming space 42
Is defined by the neck portion 43, and the passage space 44 is sealed simultaneously with the resonance muffler space 45 by joining the cylinder blocks 11A and 11B. Therefore, in forming the passage space 44, the cylinder block 1
No separate member from 1A and 11B is required, the number of parts constituting the muffler structure can be reduced, the number of assembling steps can be reduced, and the manufacturing cost of the compressor can be reduced.

(3) The inlet 46a of the discharge gas from the front discharge chamber 32 to the passage space 44 and the inlet 47a of the rear discharge chamber 33 are opposed to each other. Therefore, the two discharged gases collide with each other in the passage space 44, so that the effect of damping the pressure pulsation is further enhanced.

(4) The neck portion 43 is the outer wall surface 1 of both cylinder blocks 11A and 11B corresponding to the muffler forming space 42.
It is configured by bulging 1a toward the muffler forming space 42 side. Therefore, the number of parts can be reduced as compared with the case where the neck portion 43 is configured by a member separate from the cylinder blocks 11A and 11B. Also, the cylinder block 11
By bulging the outer wall surfaces 11a of A and 11B toward the muffler forming space 42 side, the bulging portion becomes thick, and the bulging portion 4 is formed.
The introduction passage 49 could be formed on the back side of the neck portion 43 without raising the height of 1A and 41B. Therefore, the space inside the compressor can be effectively used, and the size of the compressor can be reduced.

(Other Example) The following embodiments can be carried out without departing from the spirit of the present invention. (1) In the above-described embodiment, the discharge muffler that reduces the pressure pulsation of the discharge gas is embodied, but the present invention is not limited to this, and it is embodied as an intake muffler that reduces the pressure pulsation of the suction gas. Is also good. Further, it may be embodied in a device having both an intake muffler and an ejection muffler. With this configuration, the pressure pulsation of the suction gas can be reduced, and the vibration and noise caused by the pressure pulsation can be reduced.

(2) A plurality of resonance muffler spaces 45 are arranged in parallel with the passage space 44. In this way, the effect of damping the pressure pulsation of the discharge gas is further enhanced, and the vibration and noise caused by it can be effectively reduced.

(3) The muffler forming space 42 is formed in only one of the front side or rear side bulging portions 41A, 41B,
The other bulging portions 41B and 41A are provided in the muffler forming space 42.
Use only a lid structure that seals the opening.

(4) A muffler structure similar to that of the above embodiment is formed between the front housing 12 and the front cylinder block 11A or between the rear housing 14 and the rear cylinder block 11B.

(5) A muffler structure similar to that of the above-described embodiment is constructed so as to extend from the front housing 12 to the rear cylinder block 11B or to extend from the front cylinder block 11A to the rear housing 14. In this case, the bulged portion integrally formed with the front side cylinder block 11A (in the case of the former) or the rear side cylinder block 11B (in the case of the latter) forms a muffler that is open toward both the front side and the rear side. Space is provided.

(6) A muffler structure similar to that of the above-described embodiment is constructed so as to extend from the front housing 12 to the rear housing 14. In this case, both cylinder blocks 1
A muffler forming space that is open toward both the front side and the rear side is provided in the bulging portion integrally formed with 1A and 11B.

(7) As another piston type compressor, for example, a single piston type compressor having a single head type piston or a wave cam type compressor having a wave cam in place of the swash plate is used as the muffler structure. Be embodied in. By embodying it in the muffler structure of the piston type compressor in which the pressure pulsation of the discharge gas is large, the effect of reducing vibration and noise is effectively exhibited. Note that the muffler structure is not limited to the piston compressor, and may be embodied as a rotary compressor, for example, in a muffler structure of a vane compressor, a scroll compressor, or the like.

(Supplementary Note) The technical idea that can be understood from the above embodiment will be described. (1) The compression mechanism forms the cylinder bores 21 in the cylinder blocks 11A and 11B, which are housing components, accommodates the piston 22 in the cylinder bore 21 so that the piston 22 can reciprocate, and rotates the cam body 26. The piston 22 is reciprocated to suck the refrigerant gas and compress it,
Configuration der luma hula structure further discharges.

Particularly, in the piston type compressor in which the pulsation of the suction gas or the discharge gas is large, the effect of damping the pressure pulsation is large. (2) The neck portion 43 has an inner surface 1 in the muffler forming space 42.
By swelling 1a, the housing structure 11A, 11
B luma hula structure are integrally formed.

In this way, the housing structure 11
The number of parts can be reduced as compared with the case where the neck portion 43 is configured by a member different from A and 11B. (3) The muffler structure according to appendix (2), in which the bulging is the outer wall surface 11a of the housing constituting bodies 11A and 11B that form the muffler forming space 42.

In this way, the housing structure 11
In A and 11B, a space (thickness portion) for forming a passage or the like can be secured on the back side of the muffler forming space 42, and the space inside the compressor can be effectively used.

[0046]

According to the invention of claim 1 having the above-mentioned structure, the muffler space can be constructed with a small number of parts, and the pressure pulsation of the suction gas or the discharge gas can be sufficiently attenuated.
Not necessarily accompanied by large capacity. Therefore, the compressor can be downsized and the manufacturing cost can be reduced.

Further, to be configured the passage space with a small number of parts, it requires only a assembling step number also less because they are sealed simultaneously with the resonance muffler space. According to the invention of claim 2, the effect of damping the pressure pulsation of the discharge gas is further enhanced.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a double-headed piston type compressor.

FIG. 2 is an end view of a rear cylinder block.

FIG. 3 is a sectional view corresponding to line AA in FIG.

[Explanation of symbols]

11A, 11B ... Cylinder block as a housing structure, 22 ... Piston constituting compression mechanism, 26 ... Similarly swash plate, 41A, 41B ... Swelling part, 42 ... Muffler forming space, 45 ... Resonance muffler space.

─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Satoko Yokoyama 2-chome, Toyota-cho, Kariya City, Aichi Prefecture Toyota Industries Corporation (56) Reference JP-A-8-35485 (JP, A) 8-105381 (JP, A) Actual development Sho 60-152077 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F04B 39/00 101 F04B 27/08

Claims (2)

(57) [Claims] 1. A compressor having a structure in which a compression mechanism is housed in a housing formed by joining a plurality of housing constituents, and a refrigerant gas or the like is sucked and compressed by the operation of the compression mechanism and further discharged. in the form the muffler forming space outside the housing member, the muffler space formed by sealing the joint of the housing member between the opening of the muffler forming space is formed,
The muffler forming space bulges the housing structure inward
Through the neck formed by
The resonance muffler is composed of a road space and a resonance muffler space.
And the passage space in the circumferential direction of the housing structure.
A muffler structure characterized by being installed alongside . 2. The compression mechanism is a housing structure.
Cylinder block formed on the cylinder block
A double-headed pist that is housed in a Linda bore and reciprocates.
The piston bore and the cylinder bore.
Discharge gas discharged from the compression chamber formed surrounded by
And is surrounded by the other piston end face and the cylinder bore.
The discharge gas discharged from the compression chamber formed by
It is configured to meet in the passage space and
From the inlet of the discharge gas from the compression chamber side and from the other compression chamber side
The discharge gas inlet should face the same passage space.
And the one inlet is connected to the front housing.
Is provided at the joining portion of the
The muffler structure according to claim 1, wherein the muffler structure is provided at a joint portion with the groove .