JP2007146754A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of reducing a quantity of oil flowing out of a bleeding passage. <P>SOLUTION: An inlet port 61 of the bleeding passage 31 establishing communication between a crank chamber 5 and a suction chamber 7 is constructed as a cylindrical part provided on the end face 2f of the cylinder block 2 and projecting over an outer circumference side 64. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a compressor.

  In the compressor, the lubricating oil is stored in the crank chamber in order to supply the lubricating oil to each sliding component in the crank chamber. For example, as disclosed in Patent Document 1, this type of compressor has a crank. Since the extraction passage communicating the chamber and the suction chamber is provided, the lubricating oil flows out from the crank chamber to the suction chamber through the extraction passage. When the lubricating oil flows out of the crank chamber in this way, the following two problems are mainly caused.

First, there is a shortage of remaining oil in the crank chamber, which adversely affects sliding parts in the crank chamber. Secondly, the lubricating oil that has flowed into the suction chamber flows together with the refrigerant as a heat exchanger (for example, a condenser, an evaporator) when flowing in the suction chamber → cylinder bore → discharge chamber → outside the compressor (refrigeration cycle) → inside the compressor (suction chamber). ) And the heat exchange efficiency of the heat exchanger is reduced.
JP-A-62-203980 JP-A-4-74549

  The present invention has been made based on such a conventional technique, and an object of the present invention is to provide a compressor capable of reducing the amount of oil outflow from the extraction passage.

The invention according to claim 1 is a compressor, wherein the cylinder block has a cylinder bore that reciprocally accommodates a piston, a suction chamber provided on a top dead center side of the cylinder bore, and a top dead center of the cylinder bore. A discharge chamber provided on the point side, the crank chamber provided on the bottom dead center side of the cylinder bore, a drive shaft rotatable in the crank chamber, and a rotation of the drive shaft provided in the crank chamber. A conversion mechanism that converts the reciprocating motion of the piston, and a bleed passage that communicates the crank chamber and the suction chamber,
The inlet portion of the bleed passage is configured as a cylindrical portion provided on the end face of the cylinder block and projecting from the outer peripheral portion.

  Invention of Claim 2 is a compressor of Claim 1, Comprising: The throttle part set to the minimum passage cross-sectional area among this bleed passage is provided in the middle of the said bleed passage, The said throttle part is It is provided at a position other than the inlet opening end of the extraction passage.

A third aspect of the present invention is the compressor according to the second aspect, wherein the cylinder block is joined to a top dead center side of the cylinder block via a valve plate, and the suction chamber and the discharge chamber are formed therein. With a rear head,
The valve plate defines the cylinder bore, the suction chamber, and the discharge chamber, and includes a suction hole that communicates the cylinder bore and the suction chamber, and a discharge hole that communicates the cylinder bore and the discharge chamber. ,
The throttle part of the extraction passage is provided in a plate-like member interposed between the cylinder block and the rear head.

  A fourth aspect of the present invention is the compressor according to the third aspect, wherein the throttle portion of the extraction passage is interposed between the valve plate and the cylinder block and opens and closes the suction hole. It is provided on a suction valve plate having a valve-type suction valve.

  A fifth aspect of the present invention is the compressor according to the third aspect, wherein the throttle portion of the extraction passage is provided in the valve plate.

  The invention according to claim 6 is the compressor according to claim 3, wherein the throttle portion of the extraction passage is interposed between the valve plate and the rear head and opens and closes the discharge hole. A suction valve plate having a discharge valve of the type is provided.

  A seventh aspect of the present invention is the compressor according to the third aspect, wherein the throttle portion of the extraction passage is provided in a gasket interposed between the valve plate and the rear head. And

  The invention according to claim 8 is the compressor according to claim 3, wherein the throttle portion of the extraction passage is provided in a gasket interposed between the valve plate and the cylinder block. Features.

  According to the first aspect of the present invention, it is possible to prevent the inlet portion of the extraction passage from being buried in the film-like lubricating oil attached to the end face of the cylinder block. In addition, the lubricating oil adhering to the end face of the cylinder block hangs down due to its own weight, but at this time it bypasses the cylindrical inlet part of the bleed passage and hangs downward, so the inlet opening end of the bleed passage is opened. Lubricating oil flowing (sagging) on the front end surface of the cylindrical portion that is reduced is reduced. As a result, the amount of lubricating oil that is drawn into the refrigerant gas flowing into the inlet opening end of the extraction passage and flows into the extraction passage is reduced, and the amount of lubricating oil that is taken out of the crank chamber is reduced.

  According to the invention of claim 2, since the throttle portion of the extraction passage is provided at a position other than the inlet opening end of the extraction passage, compared to the structure in which the throttle portion is provided at the inlet opening end of the extraction passage, Since the flow velocity of the refrigerant gas passing through the inlet opening end becomes slow, the force for drawing the lubricating oil into the extraction passage at the inlet opening end becomes weak. Therefore, the amount of lubricating oil in the crank chamber can be further increased.

  According to the invention of claim 3, the processing of the drawn portion becomes easy and the manufacturing cost can be reduced.

  According to the invention of claim 4, the effect of the invention of claim 3 is obtained.

  According to the invention of claim 5, the effect of the invention of claim 3 is obtained.

  According to the invention of claim 6, the effect of the invention of claim 3 can be obtained.

  According to the invention of claim 7, the effect of the invention of claim 3 can be obtained.

  According to the invention of claim 8, the effect of the invention of claim 3 can be obtained.

  Hereinafter, a compressor according to an embodiment of the present invention will be described with reference to the drawings.

"Overall structure of compressor"
FIG. 1 is an overall sectional view of the compressor.

  The compressor 1 of this embodiment is a swash plate type variable capacity compressor as shown in FIG. The compressor 1 includes a cylinder block 2 having a plurality of cylinder bores 3 arranged at equal intervals in the circumferential direction, and a crank chamber 5 joined to the front end surface 2f of the cylinder block 2 and communicated with the cylinder bore 3 therein. And a rear head 6 joined to the rear end surface 2r of the cylinder block 2 via a valve plate 9 and forming a suction chamber 7 and a discharge chamber 8 therein. The cylinder block 2, the front head 4, and the rear head 6 are fastened and fixed by a plurality of through bolts 13 to constitute a housing of the entire compressor.

  The valve plate 9 includes a suction hole 11 that communicates the cylinder bore 3 and the suction chamber 7, and a discharge hole 12 that communicates the cylinder bore 3 and the discharge chamber 8.

  A metal intake valve plate 53 is laminated on the cylinder block 2 side of the valve plate 9. The suction valve plate 53 has a reed valve type suction valve 53v at a position corresponding to the suction hole 11, and the suction hole 11 can be opened and closed by the suction valve 53v.

  On the other hand, on the rear head 6 side of the valve plate 9, a metal discharge valve plate 54 and a retainer 55 that holds the discharge valve plate 54 between the valve plate 9 are stacked and It is fixed to the valve plate 9. The discharge valve plate 54 has a reed valve type discharge valve 54v at a position corresponding to the discharge hole 12, and the discharge hole 12 can be opened and closed by the discharge valve 54v. The discharge valve 54v is restricted in its open limit position by a retainer 55.

  Between the joint surfaces of the valve plate 9 and the rear head 6, a sheet-like gasket 57 made of a material such as synthetic rubber is interposed, and the airtightness of the suction chamber 7 and the discharge chamber 8 is ensured. Further, an O-ring 58 serving as a seal member is sandwiched between the joint surfaces of the cylinder block 2 and the rear head 6 on the outer peripheral edge side of the valve plate 9, thereby leaking refrigerant from the joint surface to the outside of the compressor. Is prevented.

  A drive shaft 10 is pivotally supported through radial bearings 15, 18 in the central through holes 14, 17 of the cylinder block 2 and the front head 4, so that the drive shaft 10 can rotate within the crank chamber 5. . A thrust bearing 19 is interposed between the front end surface of the rotor 21 fixed to the drive shaft 10 and the inner wall surface of the front head 4, and a step surface (thrust receiving surface) formed in the through-hole 14 of the cylinder block 2. Surface) and a step surface (thrust receiving surface) formed at the rear end portion of the drive shaft 10, a thrust bearing 16 is interposed. As a result, the movement of the drive shaft 10 in the axial direction is restricted.

  A conversion mechanism 20 that converts the rotation of the drive shaft 10 into the reciprocating motion of the piston 29 is provided in the crank chamber 5. The conversion mechanism 20 includes a rotor 21 as a rotating member fixed to the drive shaft 10, a sleeve 22 slidably mounted on the drive shaft 10, and a slant mounted on the sleeve 22 so as to be tiltable by a pin 23. And a rotating swash plate 24 as a plate. The rotary swash plate 24 is attached to the drive shaft 10 via the sleeve 22 and the pin 23 so that it can tilt with respect to the drive shaft 10 and slide in the axial direction of the drive shaft 10. In this example, the rotary swash plate 24 includes a hub 25 attached to the sleeve 22 so as to be tiltable and rotatable, and a substantially disc-like swash plate body 26 fixed to a boss portion 25a of the hub 25. Prepare.

  A connecting mechanism 40 is interposed between the rotor 21 and the rotating swash plate 24, and the connecting mechanism 40 allows the rotational swash plate 24 to rotate the rotating torque of the rotor 21 while allowing the tilt angle of the rotating swash plate 24 to vary. Can be communicated to.

  The inclination angle of the rotary swash plate 24 decreases when the sleeve 22 moves closer to the cylinder block 2, and decreases when the sleeve 22 moves away from the cylinder block 2. The inclination angle increases.

  The piston 29 slidably accommodated in each cylinder bore 3 is connected to the rotary swash plate 24 via a pair of hemispherical piston shoes 28, 28. When the rotary swash plate 24 rotates, the rotation of the rotary swash plate 24 is converted into a reciprocating motion of the piston 29 via the pair of piston shoes 28, 28. When the piston 29 reciprocates in the cylinder bore 3, the refrigerant in the suction chamber 7 is sucked into the cylinder bore 3 through the suction hole 11 of the valve plate 9 and then compressed in the cylinder bore 3, and the compressed refrigerant is compressed in the valve plate 9. Are discharged into the discharge chamber 8 through the discharge holes 12.

"Control of variable capacity"
In order to change the discharge capacity of the refrigerant, the piston stroke is changed by changing the inclination angle of the rotary swash plate 24. More specifically, the piston stroke is changed by changing the tilt angle of the rotary swash plate 24 by the differential pressure (pressure balance) between the crank chamber pressure Pc on the rear surface side of the piston 29 and the suction chamber pressure Ps on the front surface side of the piston 29. Let For this reason, the variable capacity compressor is provided with a pressure adjusting mechanism 30. The pressure adjusting mechanism 30 is provided in the middle of the air supply passage 32, an extraction passage 31 that connects the crank chamber 5 and the suction chamber 7, an air supply passage 32 that connects the crank chamber 5 and the discharge chamber 8. And a control valve 33 that controls opening and closing of the air passage 32.

  Since the crank chamber 5 is filled with blow-by gas from the cylinder bore 3, the crank chamber 5 is higher in pressure than the suction chamber 7 and lower in pressure than the discharge chamber 8. Therefore, the refrigerant gas in the crank chamber 5 always flows out to the suction chamber 7 through the extraction passage 31.

  When the air supply passage 32 is closed by the control valve 33, the refrigerant gas escapes from the crank chamber 5 to the suction chamber 7 through the extraction passage 31 that is always in communication, so that the pressure difference between the suction chamber 7 and the crank chamber 5 gradually increases. It disappears and pressure equalizes. Then, while the sleeve 22 moves away from the cylinder block 2, the inclination angle of the rotary swash plate 24 increases, the piston stroke increases, and the discharge amount increases.

  On the other hand, when the supply passage 32 is opened by the control valve 33, high-pressure refrigerant gas flows from the discharge chamber 8 through the supply passage 32 into the crank chamber 5, thereby increasing the pressure in the crank chamber 5. When the pressure in the crank chamber 5 increases, the inclination angle of the rotary swash plate 24 decreases while the sleeve 22 moves closer to the cylinder block 2 side, whereby the piston stroke becomes smaller and the discharge amount decreases.

"Bleeding passage"
Next, the extraction passage 31 will be described.

  The bleed passage 31 of the present embodiment includes a through passage 2s formed through the cylinder block 2 in the axial direction, a through hole 53s formed through the intake valve plate 53, and a through hole 9s formed through the valve plate 9. And is configured. The through passage 2s, the through hole 53s, and the through hole 9s are overlapped in the axial direction of the drive shaft 10 and communicate with each other to communicate the crank chamber 5 and the suction chamber 7.

  The inlet portion 61 of the bleed passage 31 (that is, the inlet portion of the through passage 2s of the cylinder block 2) is provided on the end surface (the front end surface 2f in this example) facing the crank chamber 5 among the end surfaces of the cylinder block 2. The inlet portion 61 is configured as a cylindrical portion that protrudes in a cylindrical shape in the axial direction from the front end surface 2 f of the cylinder block 2.

  Further, in the middle of the extraction passage 31, a throttle portion 65 having a passage area smaller than the general portion of the extraction passage 31 is provided. The throttle 65 limits the amount of refrigerant flowing through the extraction passage 31. In the present embodiment, the throttle portion 65 is provided in the middle of the through passage 2s of the cylinder block 2, and is separated from the inlet opening end 31a of the through passage 2s, that is, the inlet opening end 31a of the extraction passage 31.

  The liquid refrigerant and lubricating oil stored in the bottom of the crank chamber 5 are blown off by the rotational centrifugal force while being scooped up by the rotation of the conversion mechanism 20 (mainly the rotor 21 and the rotating swash plate 24) during the operation of the compressor. Part of the crank chamber 5 adheres to the wall surface of the crank chamber 5 and part of the crank chamber 5 fills in a mist shape. The lubricating oil adhering to the wall surface of the crank chamber 5 exists in a film shape with a thickness.

  Here, the inlet portion 61 of the bleed passage 31 protrudes in a cylindrical shape from the outer peripheral side portion 64, so that it is prevented from being buried in the film-like lubricating oil adhering to the front end surface 2 f of the cylinder block 2. The Further, the lubricating oil adhering to the front end surface 2f of the cylinder block 2 hangs down due to its own weight, but at this time, the lubricating oil hangs down around the tubular portion 61 as shown in FIG. Therefore, the lubricating oil adhering to the front end surface 61a of the cylindrical part 61 or the lubricating oil flowing (dripping) on the front end surface 61a is reduced.

  Thereby, the lubricating oil which exists in the vicinity of the inlet opening end 31a of the extraction passage 31 decreases. Therefore, the amount of lubricating oil drawn into the extraction passage 31 by being drawn into the refrigerant gas flowing into the inlet opening end 31a of the extraction passage 31 is reduced. In other words, the amount of lubricating oil taken out from the crank chamber 5 to the suction chamber 7 is reduced.

"effect"
Next, the effects of this embodiment are listed.

  (1) According to this embodiment, the inlet portion 61 of the extraction passage 31 that communicates the crank chamber 5 and the suction chamber 7 is provided on the end surface 2f of the cylinder block 2 and protrudes from the outer peripheral portion thereof. It is constituted as a cylindrical part.

  Therefore, it is possible to prevent the inlet portion 61 of the extraction passage 31 from being completely buried in the film-like lubricating oil attached to the end surface 2 f of the cylinder block 2. Further, the lubricating oil adhering to the end surface 2f of the cylinder block 2 hangs down due to its own weight, but at this time, the lubricating oil hangs down around the cylindrical inlet 61 of the bleed passage 31, so the bleed passage 31 Less lubricating oil flows down the vicinity of the inlet opening end 31a (tip surface 61a of the cylindrical portion 61).

  Thereby, the lubricating oil drawn into the refrigerant gas flow and flowing into the extraction passage 31 from the inlet opening end 31a of the extraction passage 31 is reduced, and the amount of the lubricating oil taken out from the crank chamber 5 to the suction chamber 7 is reduced. . Thus, the amount of lubricating oil taken out of the crank chamber 5 is reduced, so that the amount of lubricating oil in the crank chamber 5 is kept large, and the lubricity of the sliding parts in the crank chamber 5 is well maintained.

  (2) Further, according to the present embodiment, the throttle portion 65 set to the minimum passage cross-sectional area of the extraction passage 31 is provided in the middle of the extraction passage 31 at a position other than the inlet opening end 31 a of the extraction passage 31. ing.

  If the throttle portion is provided at the inlet opening end 31 a of the extraction passage 31, the flow rate of the refrigerant gas when passing through the inlet opening end 31 a increases, so that the lubricating oil is introduced from the crank chamber 5 into the extraction passage 31. The power to pull in becomes stronger. However, in the present embodiment, as described above, the throttle portion 65 is provided at a portion other than the inlet opening end 31a of the extraction passage 31, so that the amount of lubricating oil in the crank chamber 5 can be further increased.

  (3) Moreover, according to this embodiment, the outer peripheral surface 61b of the cylindrical inlet part 61 of the extraction passage 31 and the surrounding surface 64 intersect at a right angle or an angle close to a right angle. Therefore, as compared with a structure in which the outer peripheral surface 61b of the cylindrical inlet portion 61 of the extraction passage 31 is formed in, for example, a flare shape or a taper shape, the lubricating oil flowing down the end surface 2f of the cylinder block 2 is It becomes difficult to ride on the front end surface 61a of the inlet portion 61. Therefore, the amount of lubricating oil in the crank chamber 5 can be further increased.

  According to the first embodiment, the throttle portion 65 is provided in the cylinder block 2. However, for example, as in the fourth to sixth embodiments described later, it is provided in a portion other than the cylinder block 2. Manufacturing is easy and preferable.

  Other embodiments will be described below, but the same reference numerals are given to the same configurations as those of the above-described embodiments, and descriptions of the configurations and functions and effects are omitted.

(Second Embodiment)
In the second embodiment shown in FIG. 3, a passage enlargement portion 67 having a passage cross-sectional area larger than the general portion of the extraction passage 31 is provided at the inlet opening end 31 a of the extraction passage 31. Therefore, the flow rate of the refrigerant gas flowing through the extraction passage 31 becomes slow at the inlet opening end 31 a of the extraction passage 31. Thereby, the amount of lubricating oil drawn into the extraction passage 31 from the inlet opening end 31a of the extraction passage 31 is reduced. Therefore, more lubricating oil in the crank chamber 5 can be maintained.

(Third embodiment)
The third embodiment shown in FIG. 4 is different from the first embodiment in that the outer peripheral surface 61b of the inlet portion 61 of the extraction passage 31 is a step. Also in the third embodiment, the same operational effects as those of the first embodiment can be obtained. Note that when the step is formed at a right angle or an angle close to a right angle as in the third embodiment, the lubricating oil adhering to the end surface 2f of the cylinder block 2 is removed from the tip surface 61a of the cylindrical inlet portion 61. This is preferable because the probability of getting on the vehicle becomes low.

(Fourth embodiment)
The fourth embodiment shown in FIG. 5 differs from the first embodiment in that a throttle member 65 of the extraction passage 31 is provided in a plate-like member interposed between the cylinder block 2 and the rear head 6. . More specifically, in the fourth embodiment, the throttle portion 65 is provided on the intake valve plate 53. Therefore, compared with the case where the throttle part 65 is formed in the cylinder block 2 as in the first embodiment, manufacturing is easy and preferable.

(Fifth embodiment)
In the fifth embodiment shown in FIG. 6 as well, the throttle portion 65 of the extraction passage 31 is provided in a plate-like member interposed between the cylinder block 2 and the rear head 6. More specifically, the throttle portion 65 is provided in the valve plate 9 in the fifth embodiment. Therefore, compared with the case where the throttle part 65 is formed in the cylinder block 2 as in the first embodiment, manufacturing is easy and preferable.

(Sixth embodiment)
In the sixth embodiment shown in FIG. 7 as well, a throttle member 65 of the extraction passage 31 is provided in a plate-like member interposed between the cylinder block 2 and the rear head 6. More specifically, in the sixth embodiment, the throttle portion 65 is provided on a gasket 57 interposed between the valve plate 9 and the rear head 6. Therefore, compared with the case where the throttle part 65 is formed in the cylinder block 2 as in the first embodiment, manufacturing is easy and preferable.

  Although not shown, the same effect as in the fourth to sixth embodiments can be obtained even if the throttle portion 65 is provided in a gasket interposed between the valve plate 9 and the cylinder block 2. Although not shown in the drawing, the same effect can be obtained by providing the throttle 65 on the intake valve plate 53 interposed between the valve plate 9 and the rear head 6.

  It should be noted that the present invention should not be construed as limited to the above-described embodiments.

  For example, as shown in FIG. 8, the throttle portion 65 of the extraction passage 31 may be provided in the rear head 6.

  Further, as shown in FIG. 9, through bolts formed through the cylinder block 2 and the rear head 6 and the plate-like members (9, 53, 54, 57) interposed therebetween to allow the through bolts 13 to pass therethrough. The hole 71 may be configured as the bleed passage 31 and the inlet 61 of the bleed passage 31 may be formed in a cylindrical shape as in the above-described embodiment.

  Further, the inlet portion of the extraction passage is not limited to a cylindrical shape with a circular cross section, and may be a cylindrical shape with a polygonal cross section, or may have another cross sectional shape.

  The configuration of the conversion mechanism 20 can be changed to other configurations as long as the rotation of the drive shaft is converted into the rotation of the piston. Various other modifications are possible within the scope of the technical idea of the present invention.

Sectional drawing of the compressor concerning 1st Embodiment of this invention. The front view of the cylinder block of the compressor. Sectional drawing of the vicinity of the extraction passage of the compressor of 2nd Embodiment of this invention. Sectional drawing of the vicinity of the extraction passage of the compressor of 3rd Embodiment of this invention. Sectional drawing of the vicinity of the extraction passage of the compressor of 4th Embodiment of this invention. Sectional drawing of the vicinity of the extraction passage of the compressor of 5th Embodiment of this invention. Sectional drawing of the vicinity of the extraction passage of the compressor of 6th Embodiment of this invention. Sectional drawing of the vicinity of the extraction passage of the compressor of 6th Embodiment of this invention. Sectional drawing of the vicinity of the extraction passage of the compressor of 6th Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Compressor 2 ... Cylinder block 2f ... Front end surface (end surface)
2r ... Rear end face 3 ... Cylinder bore 4 ... Front head 5 ... Crank chamber 6 ... Rear head 7 ... Suction chamber 8 ... Discharge chamber 9 ... Valve plate 10 ... Drive shaft 11 ... Suction hole 12 ... Discharge hole 20 ... Conversion mechanism 29 ... Piston 31 ... Extraction passage 31a ... Open end 53 ... Suction valve plate 53v ... Suction valve 54 ... Discharge valve plate 54v ... Discharge valve 57 ... Gasket 61 ... Inlet part (tubular part)
61a ... distal end surface 61b ... outer peripheral surface 64 ... outer peripheral side portion 65 ... throttle part 67 ... passage expanding part

Claims (8)

A cylinder block (2) having a cylinder bore (3) for reciprocally accommodating the piston (29);
A suction chamber (7) provided on the top dead center side of the cylinder bore (3);
A discharge chamber (8) provided on the top dead center side of the cylinder bore (3);
The crank chamber (5) provided on the bottom dead center side of the cylinder bore (3);
A drive shaft (10) rotatable in the crank chamber (5);
A conversion mechanism (20) provided in the crank chamber (5) and converting the rotation of the drive shaft (10) into a reciprocating motion of the piston (29);
An extraction passage (31) communicating the crank chamber (5) and the suction chamber (7);
With
The inlet portion (61) of the bleed passage (31) is configured as a cylindrical portion provided on the end surface (2f) of the cylinder block (2) and projecting from the outer peripheral side portion (64). The compressor characterized by having. The compressor according to claim 1,
In the middle of the extraction passage (31), a throttle part (65) set to the minimum passage cross-sectional area of the extraction passage (31) is provided,
The said throttle part (65) is provided in positions other than the inlet opening end (31a) of the said extraction passage (31), The compressor characterized by the above-mentioned. The compressor according to claim 2,
A rear head (6) joined to the top dead center side of the cylinder block (2) via a valve plate (9) and forming the suction chamber (7) and the discharge chamber (8) therein;
The valve plate (9) defines the cylinder bore (3), the suction chamber (7), and the discharge chamber (8), and communicates the cylinder bore (3) and the suction chamber (7). A discharge hole (12) communicating the hole (11), the cylinder bore (9), and the discharge chamber (8);
The throttle part (65) is provided on a plate-like member (9, 53, 54, 57,...) Interposed between the cylinder block (2) and the rear head (6). Compressor. The compressor according to claim 3, wherein
The throttle part (65) of the bleed passage (31) has a reed valve type suction valve (53v) interposed between the valve plate (9) and the cylinder block (2) and opening and closing the suction hole. A compressor characterized in that it is provided on a suction valve plate (53). The compressor according to claim 3, wherein
The compressor, wherein the throttle part (65) of the extraction passage (31) is provided in the valve plate (9). The compressor according to claim 3, wherein
The throttle part (65) of the bleed passage (31) is interposed between the valve plate (9) and the rear head (6) and is a reed valve type discharge valve (54v) that opens and closes the discharge hole (12). The compressor is provided on a suction valve plate (54) having a). The compressor according to claim 3, wherein
A compressor, wherein the throttle part (65) of the extraction passage (31) is provided in a gasket (57) interposed between the valve plate (9) and the rear head (6). The compressor according to claim 3, wherein
The compressor according to claim 1, wherein the throttle portion (65) of the extraction passage (31) is provided in a gasket interposed between the valve plate (9) and the cylinder block (2).

Images