JP2005042624A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of reducing pressure pulsation and noise and preventing an intake efficiency from lowering. <P>SOLUTION: This compressor is formed such that a front housing 4 is joined to the front end face of a cylinder block 2 having a cylinder bore 3 to form a crank chamber 5 and a rear housing 6 is joined to the rear end face of the cylinder block 2 through a valve plate 9 to form an intake chamber 7 and a discharge chamber 8, and a piston 29 is reciprocated by utilizing the rotation of a drive shaft S pivotally supported on the inside of the crank chamber 5. In this compressor, the intake chamber 7 is formed of a first intake chamber 7a allowed to communicate with an intake port 16 into which a refrigerant is supplied from the outside and a second intake chamber 7b allowed to communicate with a cylinder bore 3 through a valve plate. The first intake chamber 7a is separated from the second intake chamber 7b through a partition wall 10, and at least two communication passages 13 are formed in the partition wall 10 to communicate the first intake chamber 7a with the second intake chamber 7b. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a compressor that adiabatically compresses refrigerant evaporated in a refrigeration cycle.

In a compressor that is interposed in a refrigeration cycle such as a vehicle air conditioner and adiabatically compresses the refrigerant vaporized in the refrigeration cycle, a plurality of bores are arranged in parallel as shown in Patent Document 1, for example. And a cylinder head that closes the outer end of the cylinder block while sandwiching a valve plate having a suction port and a discharge port corresponding to each bore, and a piston inserted in each bore has a predetermined phase difference. For a compressor that reciprocates with a cylinder, a discharge chamber is provided in the central area of the cylinder head, a suction chamber is provided in the outer peripheral area thereof, and a plurality of areas in the suction chamber are provided via a suction hole and a guide hole. And a suction flange connected to the refrigeration circuit directly communicate with each other to reduce the pressure loss in the suction chamber and to equalize the pressure difference of the suction refrigerant gas.
JP-A-6-317249

  In a reciprocating compressor including such a compressor, pressure pulsation occurs in the refrigerant when the piston reciprocates. Further, since the rotational speed of the compressor changes according to the rotational speed of the engine, the pressure pulsation frequency also changes according to the rotational speed of the compressor. And since the natural frequency of the compressor and the natural frequency of the auxiliaries that make up the refrigeration cycle are relatively close, when the compressor approaches a certain number of revolutions, the compressor and the auxiliary device resonate due to the pressure pulsation of the refrigerant. As a result, there is a problem that abnormal noise occurs or pressure pulsation becomes a suction resistance when the refrigerant is sucked into the compressor, and the suction efficiency is lowered.

  Accordingly, an object of the present invention is to provide a compressor that can reduce pressure pulsation, reduce the occurrence of abnormal noise, and prevent a reduction in suction efficiency.

  In the first aspect of the present invention, a front housing is joined to a front end face of a cylinder block having a cylinder bore to form a crank chamber, and a rear housing is joined to a rear end face of the cylinder block via a valve plate. In a compressor that forms a suction chamber and a discharge chamber and reciprocates a piston using rotation of a drive shaft that is pivotally supported in the crank chamber, the suction chamber is communicated with a suction port to which a refrigerant is supplied from the outside. The first suction chamber and a second suction chamber communicated with the cylinder bore via the valve plate, and the first suction chamber and the second suction chamber are divided by the partition wall, and the partition wall It is characterized by being communicated by at least two or more communication paths formed in the above.

  According to a second aspect of the present invention, in the compressor according to the first aspect, one of the communication passages is formed in the partition located in front of the suction port outlet.

  According to a third aspect of the present invention, in the compressor according to the first or second aspect, the suction hole in the suction stroke in the suction hole provided in the valve plate and the valve provided in the valve plate The communication path is formed so that the total cross-sectional area of the communication path is larger than the cross-sectional area of the choke portion formed by the mechanism.

  According to a fourth aspect of the present invention, in the compressor according to any one of the first to third aspects, the outer peripheral portion of the circumferential portion of the first suction chamber having a substantially cylindrical shape has a substantially ring shape. The discharge chamber having a substantially cylindrical shape is formed between the first suction chamber and the valve plate, and at the inner peripheral portion of the second suction chamber, while the second suction chamber is provided across the partition wall. It is characterized by that.

  According to a fifth aspect of the present invention, in the compressor according to the fourth aspect, each of the suction chamber and the discharge chamber constituting the rear housing is formed by separate members.

  A sixth aspect of the present invention is the compressor according to any one of the first to fifth aspects, wherein the first suction chamber and the second suction chamber have different internal volumes. .

  According to a seventh aspect of the present invention, in the compressor according to any one of the first to sixth aspects, at least a part of the partition wall forms a suction port passage communicating the suction port and the suction chamber. And a wall surface that forms a discharge port passage that communicates the discharge port and the discharge chamber.

  According to the first aspect of the present invention, since the first suction chamber and the second suction chamber provided in the rear housing are communicated with each other by the communication path, the refrigerant supplied into the compressor has a predetermined volume. When the compressor is expanded in the first suction chamber and the second suction chamber, the pressure pulsation generated during the middle rotation operation of the compressor is reduced, and the flow rate is increased when the refrigerant passes through the communication path having a predetermined cross-sectional area. As a result, the pressure pulsation generated when the compressor operates at a low speed is reduced.

  As a result, it is possible to reduce the generation of abnormal noise in a wide range from the low rotation range to the middle rotation range of the compressor, which is particularly worrisome for the occupant, and to prevent a reduction in suction efficiency.

  According to the second aspect of the present invention, in addition to the effect of the first aspect, the refrigerant introduced into the first suction chamber from the suction port is linearly introduced into the second suction chamber through the communication path, whereby the suction port. Ventilation resistance to the suction hole disposed at a position away from the head can be reduced, and further reduction in suction resistance can be prevented.

  According to the third aspect of the present invention, in addition to the effects of the first and second aspects, the passage sectional area of the choke portion formed by the suction hole in the suction stroke and the valve mechanism provided in the valve plate. Since the communication path is formed so that the total cross-sectional area of the communication path is larger than that of the communication path, the generation of noise in the low rotation range can be reduced without the communication path becoming suction resistance.

  According to the fourth aspect of the present invention, in addition to the effects of the first to third aspects, the suction chamber having an internal volume necessary for reducing pressure pulsation without increasing the size of the entire apparatus in the radial direction. Can be formed.

  According to the fifth aspect of the invention, in addition to the effect of the fourth aspect, the suction chamber and the discharge chamber are formed of separate members, thereby simplifying the manufacturing process of the rear housing and reducing the manufacturing cost. be able to.

  According to the sixth aspect of the present invention, in addition to the effects of the first to fifth aspects, the pressure pulsation that can be eliminated by providing the first suction chamber and the second suction chamber with different internal volumes. Since the frequency range can be changed, the generation of abnormal noise in a wider rotation range can be reduced.

  According to the seventh aspect of the present invention, in addition to the effects of the first to sixth aspects, at least a part of the partition wall includes a wall surface that forms a suction port passage communicating the suction port and the suction chamber, a discharge port, and a discharge port. By forming with the wall surface which forms the discharge port channel | path which connects a chamber, the suction chamber provided with required internal volume can be formed, without enlarging the whole compressor.

  Hereinafter, a compressor according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is an overall cross-sectional view of a compressor according to a first embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along line AA of FIG. The compressor 1 according to the first embodiment is a swash plate type variable capacity compressor, which is used, for example, in a cooling cycle of a vehicle air conditioner and adiabatically compresses refrigerant gas evaporated in a refrigeration cycle.

  As shown in FIGS. 1 and 2, the variable capacity compressor 1 is joined to a cylinder block 2 having 6 cylinder bores 3 arranged at equal intervals in the circumferential direction, and a front end face of the cylinder block 2. The front housing 4 that forms the crank chamber 5 between the cylinder block 2 and the rear housing 6 that is joined to the rear end surface of the cylinder block 2 via the valve plate 9 to form the suction chamber 7 and the discharge chamber 8. It is mainly composed. The cylinder block 2, the front housing 4, and the rear housing 6 are fastened and fixed by a plurality of through bolts B.

  The valve plate 9 is provided with a suction hole 11 for communicating the cylinder bore 3 and the suction chamber 7, and a discharge hole 12 for communicating the cylinder bore 3 and the discharge chamber 8, one for each cylinder bore 3.

  A suction side reed valve 14 for opening and closing the suction hole 11 is provided as a valve mechanism on the cylinder block 2 side of the valve plate 9, while a discharge side for opening and closing the discharge hole 12 is provided on the rear housing 6 side of the valve plate 9. A reed valve 15 is provided. A gasket is sandwiched between the valve plate 9 and the rear housing 6 to maintain the airtightness of the suction chamber 7 and the discharge chamber 8. In addition, an O-ring is sandwiched around the joint surface between the rear housing 6 and the cylinder block 2 at the periphery of the valve plate 9 to prevent the refrigerant from leaking out of the compressor 1.

  A drive shaft S is rotatably supported via bearings in the support holes 19 and 20 at the centers of the cylinder block 2 and the front housing 4.

  In the crank chamber 5, a drive plate 21 fixed to the drive shaft S, a journal 24 slidably connected to a sleeve 22 slidably fitted on the drive shaft S by a pin 23, and this A wobble plate (swash plate) 26 mounted on a boss portion 25 of the journal 24 via a bearing is disposed. The wobble plate 26 is slidably connected to a restriction plate 35 fixed in the crank chamber 5, thereby preventing rotation and swinging in the axial direction. That is, when the journal 24 rotates by rotating the drive shaft S, the wobble plate 26 swings in the axial direction without rotating as the journal 24 rotates. The drive plate 21 and the journal 24 are connected to the hinge arms 21h and 24h via arcuate long holes 27 and pins 28, whereby the wobbling plate 26 has a maximum inclination angle and a minimum inclination angle. Is regulated.

  The pistons 29 accommodated in the respective cylinder bores 3 are connected to the wobble plate 26 via the piston rod 30, and reciprocate when the wobble plate 26 swings. The basic function of the compressor 1 is to compress the refrigerant sucked into the suction chamber 7 → the suction hole 11 of the valve plate 9 → the cylinder bore 3 by the piston movement of the piston 29, and the discharge hole 12 of the cylinder bore 3 → the valve plate 9. → The compressed refrigerant is discharged into the discharge chamber 8.

  In order to make the discharge capacity variable, the compressor 1 of the present embodiment communicates a bleed passage (not shown) that always communicates the crank chamber 5 and the suction chamber 7 with the crank chamber 5 and the discharge chamber 8. A pressure control mechanism including an air supply passage 32 and an electromagnetic control valve (not shown) as a pressure control valve for opening and closing the air supply passage 32 is provided. By opening and closing the electromagnetic control valve, the high-pressure refrigerant in the discharge chamber 8 is supplied to the crank chamber 5, and when the pressure in the crank chamber 5 changes, the pressure balance between the crank chamber 5 and the suction chamber 7 (piston 29). The inclination of the wobble plate 26 changes according to the pressure balance before and after that, that is, the piston stroke changes, and the discharge capacity of the compressor 1 changes.

  Hereinafter, the configuration of the rear housing 6 will be described in detail. As shown in FIGS. 1 and 2, the rear housing 6 of the present embodiment has a substantially cylindrical shape and is connected to a suction port 16 to which a refrigerant is supplied from an external pipe (not shown). A second suction chamber 7b having a substantially ring shape and communicating with the cylinder bore 3 via the valve plate 9 is provided on the outer peripheral portion of the circumferential portion of the chamber 7a with the partition wall 10 interposed therebetween. The first suction chamber 7a and the second suction chamber 7b communicate with each other through the three communication passages 13 formed.

  Further, the rear housing 6 is formed with a discharge chamber 8 having a substantially cylindrical shape between the first suction chamber 7a and the valve plate 9 and in the inner peripheral portion of the second suction chamber 7b, and discharges the compressed refrigerant to the discharge port. 17 is supplied to external piping. Further, the rear housing 6 is mainly composed of two members, a suction chamber side member 6a having a first suction chamber 7a and a second suction chamber 7b, and a discharge chamber side member 6b having a discharge chamber 8. It is formed by assembling the side member 6b inside the suction chamber side member 6a.

  The suction chamber side member 6a is formed so that the first suction chamber 7a and the second suction chamber 7b have different internal volumes, and the three communication passages 13 are formed in the partition wall 10 located in front of the outlet of the suction port 16. One of these is formed.

  The communication passage 13 is larger than the passage cross-sectional area of the choke portion formed by the suction hole 11 in the suction stroke in the suction hole 11 provided in the valve plate 9 and the suction side reed valve 14 provided in the valve plate 9. The communication path 13 is formed so that the total cross-sectional area of is larger.

  The refrigerant supplied from the suction port 16 to the first suction chamber 7a is expanded in the first suction chamber 7a, and then sent to the second suction chamber 7b through the communication path 13. Here, the refrigerant is temporarily increased in speed when passing through the communication passage 13, and when supplied to the second suction chamber 7b, the refrigerant expands again and the flow velocity is reduced.

  The cylinder in the suction stroke, that is, the cylinder in which the piston 29 is moved from the top dead center to the bottom dead center has a negative pressure in the cylinder, so the suction side reed valve 14 opens the suction hole 11 according to the negative pressure. . Then, the refrigerant sent into the second suction chamber 7b is supplied into the cylinder through the opened suction hole 11.

  When the piston 29 passes through the bottom dead center and shifts to the compression stroke, the refrigerant pressure in the cylinder increases. When a predetermined pressure value is exceeded, the discharge side reed valve 15 is opened, the refrigerant in the cylinder is discharged into the discharge chamber 8, and the high pressure refrigerant is supplied to the external piping through the discharge port 17.

As another aspect of the rear housing 6 of the present embodiment, there is a rear housing 6A as shown in FIGS. The rear housing 6A is different from the rear housing 6 in that the partition wall 10A communicates the wall surface 16b that forms the suction port passage 16a that connects the suction port 16A and the suction chamber 7A, the discharge port 17A, and the discharge chamber 8A. A wall surface 17b forming the discharge port passage 17a, a mounting bolt seat 6d formed on the suction chamber side member 6a for fixing the discharge chamber side member 6b to the suction chamber side member 6a with a bolt 6c, an electromagnetic control valve ( This is a point formed by a wall surface of a valve storage chamber (not shown) for storing a not shown.
With the configuration as described above, the first suction chamber 7a and the second suction chamber 7b provided in the rear housing 6 are communicated with each other by the communication passage 13, so that the refrigerant supplied into the compressor 1 has a predetermined amount. When the first suction chamber 7a and the second suction chamber 7b having a capacity are expanded, the pressure pulsation generated when the compressor 1 is in the middle rotation operation is reduced, and the refrigerant passes through the communication passage 13 having a predetermined cross-sectional area. When passing, the flow velocity is increased and the pressure pulsation generated when the compressor 1 is operating at a low speed is reduced.

  As a result, it is possible to reduce the generation of abnormal noise in a wide range from the low rotation region to the middle rotation region of the compressor 1 that is particularly worrisome for the occupant, and to prevent a reduction in suction efficiency.

  The refrigerant introduced into the first suction chamber 7a from the suction port 16 is linearly introduced into the second suction chamber 7b through the communication passage 13 and thereby reaches the suction hole 11 disposed at a position away from the suction port 16. Ventilation resistance is reduced, and further reduction in inhalation resistance can be prevented.

  The communication passage is such that the total cross-sectional area of the communication passage 13 is larger than the passage cross-sectional area of the choke portion formed by the suction hole 11 in the suction stroke and the suction-side reed valve 14 provided in the valve plate 9. Since 13 is formed, it is possible to reduce the occurrence of noise in the low rotation range without the communication path 13 becoming suction resistance.

  The suction chamber 7 having an internal volume necessary for reducing pressure pulsation can be formed without increasing the size of the entire apparatus in the radial direction.

  Since the suction chamber 7 and the discharge chamber 8 are formed of separate members, the manufacturing process of the rear housing 6 is simplified, and the manufacturing cost can be reduced.

  Since the first suction chamber 7a and the second suction chamber 7b have different internal volumes, the frequency range of the pressure pulsation that can be eliminated can be changed, so that the generation of noise in a wider rotational range is reduced. can do.

In the rear housing 6a according to another aspect, the partition wall is formed by the wall surface 16b that forms the suction port passage 16a, the wall surface 17b that forms the discharge port passage 17a, the mounting bolt seat 6d, and the valve storage chamber. As a result, a suction chamber having a required internal volume can be formed without increasing the size of the entire compressor.
Next, a compressor according to a second embodiment of the present invention will be described with reference to the drawings. The major difference between the compressor 1 'of the present embodiment and the compressor 1 of the first embodiment is that the shape of the rear housing 6' is different, and the other structure is the same as the compressor 1 of the first embodiment. Therefore, the same reference numerals are given and detailed description is omitted. FIG. 3 is a cross-sectional view along the same plane as in FIG.

  As shown in FIGS. 1 and 3, the rear housing 6 ′ of the present embodiment has a substantially ring shape at the outer peripheral portion of the circumferential portion of the first suction chamber 7 a ′ having a substantially cylindrical shape, and A second suction chamber 7b 'communicated with the cylinder bore 3 via the valve plate 9 is provided across the partition wall 10', and the first suction chamber 7a 'is formed by three communication passages 13' formed in the partition wall 10 '. And the second suction chamber 7b '.

  Further, a discharge chamber 8 'having a substantially cylindrical shape is formed in the rear housing 6' between the first suction chamber 7a 'and the valve plate 9 and in the inner peripheral portion of the second suction chamber 7b'. The refrigerant is supplied to the external pipe through the discharge port 17 ′. Further, the rear housing 6 'is mainly composed of two members: a suction chamber side member 6a' having a first suction chamber 7a 'and a second suction chamber 7b' and a discharge chamber side member 6b 'having a discharge chamber 8'. The discharge chamber side member 6b 'is assembled inside the suction chamber side member 6a'.

  A suction port 16 'to which refrigerant is supplied from an external pipe (not shown) communicates with the second suction chamber 7b', and three communication passages 13 'are connected to the partition wall 10' located in front of the outlet of the suction port 16 '. One is formed. The suction chamber side member 6a 'is formed so that the first suction chamber 7a' and the second suction chamber 7b 'have different internal volumes.

  The communication passage 13 is larger than the passage cross-sectional area of the choke portion formed by the suction hole 11 in the suction stroke in the suction hole 11 provided in the valve plate 9 and the suction side reed valve 14 provided in the valve plate 9. The communication passage 13 'is formed so that the total cross-sectional area of' becomes larger.

  The refrigerant supplied from the suction port 16 ′ to the first suction chamber 7 a ′ is expanded in the first suction chamber 7 a ′ and then sent to the second suction chamber 7 b ′ through the communication path 13 ′. Here, the refrigerant is temporarily accelerated when passing through the communication passage 13 ', and when supplied to the second suction chamber 7b', the refrigerant expands again, and the flow velocity decreases.

  The cylinder in the suction stroke, that is, the cylinder in which the piston 29 is moved from the top dead center to the bottom dead center has a negative pressure in the cylinder, so the suction side reed valve 14 opens the suction hole 11 according to the negative pressure. . Then, the refrigerant sent into the second suction chamber 7 b ′ is supplied into the cylinder through the opened suction hole 11.

  When the piston 29 passes through the bottom dead center and shifts to the compression stroke, the refrigerant pressure in the cylinder increases. When a predetermined pressure value is exceeded, the discharge-side reed valve 15 is opened, the refrigerant in the cylinder is discharged into the discharge chamber 8 ', and high-pressure refrigerant is supplied to the external piping through the discharge port 17'.

  With the configuration as described above, the first suction chamber 7a 'and the second suction chamber 7b' provided in the rear housing 6 'are communicated with each other by the communication passage 13', so that the first suction chamber 7a 'is supplied into the compressor 1'. When the refrigerant expands in the first suction chamber 7a ′ and the second suction chamber 7b ′ having a predetermined volume, the pressure pulsation generated during the middle rotation operation of the compressor 1 ′ is reduced, and the refrigerant When passing through the communication passage 13 'having an area, the flow velocity is increased, and the pressure pulsation generated when the compressor 1' operates at a low speed is reduced.

  As a result, it is possible to reduce the generation of abnormal noise over a wide range from the low rotation range to the middle rotation range of the compressor 1 'which is particularly worrisome for the occupant, and to prevent a reduction in suction efficiency.

  The total cross-sectional area of the communication passage 13 'is larger than the cross-sectional area of the choke portion formed by the suction hole 11' in the suction stroke and the suction-side reed valve 14 provided in the valve plate 9. Since the communication path 13 ′ is formed, it is possible to reduce the occurrence of abnormal noise in the low rotation range without the communication path 13 ′ becoming suction resistance.

  The suction chamber 7 'having an internal volume necessary for reducing pressure pulsation can be formed without increasing the size of the entire apparatus in the radial direction.

  Since the suction chamber 7 'and the discharge chamber 8' are formed of separate members, the manufacturing process of the rear housing 6 'is simplified, and the manufacturing cost can be reduced.

  Since the first suction chamber 7a 'and the second suction chamber 7b' have different internal volumes, the frequency range of the pressure pulsation that can be eliminated can be changed, so that abnormal noise is generated in a wider rotational range. Can be reduced.

  Next, a compressor according to a third embodiment of the present invention will be described with reference to the drawings. The major difference between the compressor 1 ″ of the present embodiment and the compressor 1 of the first embodiment is that the shape of the rear housing 6 ″ is different, and the other structure is the same as that of the compressor 1 of the first embodiment. Therefore, the same reference numerals are given and detailed description is omitted. FIG. 4 is a cross-sectional view along the same plane as in FIG.

  As shown in FIGS. 1 and 4, the rear housing 6 ″ of the present embodiment has a substantially ring shape on the outer peripheral portion of the circumferential portion of the first suction chamber 7 a ″ having a substantially cylindrical shape, and A second suction chamber 7b "communicated with the cylinder bore 3 via the valve plate 9 is provided across the partition wall 10", and the first suction chamber 7a "is formed by three communication passages 13" formed in the partition wall 10 ". And the second suction chamber 7b ″.

  Further, a discharge chamber 8 ″ having a substantially cylindrical shape is formed in the rear housing 6 ″ between the first suction chamber 7a ″ and the valve plate 9 and in the inner peripheral portion of the second suction chamber 7b ″, and is compressed. The refrigerant is supplied to the external piping through the discharge port 17 ″. Further, the rear housing 6 ″ has a suction chamber side member 6a ″ having a first suction chamber 7a ″ and a second suction chamber 7b ″ and a discharge chamber 8 ″. The discharge chamber side member 6b "is mainly composed of two members, and is formed by assembling the discharge chamber side member 6b" inside the suction chamber side member 6a ".

  A muffler chamber 18 ″ formed outside the rear housing 6 ″ and having a predetermined volume is provided with a suction port 16 ″ through which refrigerant is supplied from an external pipe (not shown). The chamber 18 "communicates with the first suction chamber 7a" through a communication passage 13a "having a predetermined passage cross-sectional area. Further, the suction chamber side member 6a ″ is formed such that the first suction chamber 7a ″, the second suction chamber 7b ″, and the muffler chamber 18 ″ have different internal volumes.

  The communication passage 13 is larger than the passage cross-sectional area of the choke portion formed by the suction hole 11 in the suction stroke in the suction hole 11 provided in the valve plate 9 and the suction side reed valve 14 provided in the valve plate 9. The communication path 13 ″ is formed so that the total cross-sectional area of ″ is larger.

  The refrigerant supplied from the suction port 16 ″ to the muffler chamber 18 ″ expands in the muffler chamber 18 ″, and then is supplied to the first suction chamber 7a ″ through the communication passage 13a ″. Then, the refrigerant is supplied to the first suction chamber 7a ″. The supplied refrigerant is expanded in the first suction chamber 7a ″ and then fed into the second suction chamber 7b ″ through the communication passage 13 ″. Here, the refrigerant passes through the communication passage 13a ″ and the communication passage 13 ″. When the speed is temporarily increased and supplied to the first suction chamber 7a ″ and the second suction chamber 7b ″, the refrigerant expands again, and the flow velocity decreases.

  The cylinder in the suction stroke, that is, the cylinder in which the piston 29 is moved from the top dead center to the bottom dead center has a negative pressure in the cylinder, so the suction side reed valve 14 opens the suction hole 11 according to the negative pressure. . Then, the refrigerant sent into the second suction chamber 7 b ″ is supplied into the cylinder through the opened suction hole 11.

  When the piston 29 passes through the bottom dead center and shifts to the compression stroke, the refrigerant pressure in the cylinder increases. When a predetermined pressure value is exceeded, the discharge-side reed valve 15 is opened, the refrigerant in the cylinder is discharged into the discharge chamber 8 ", and the high-pressure refrigerant is supplied to the external piping through the discharge port 17".

  With the above-described configuration, the muffler chamber 18 ″ provided in the rear housing 6 ″ and the first suction chamber 7a ″ are communicated with each other through the communication passage 13a ″, and the first suction chamber 7a ″ and the second suction chamber 7b ″ are communicated with each other. Are communicated by the communication passage 13 ″, the refrigerant supplied into the compressor 1 ″ has a predetermined volume in the muffler chamber 18 ″, the first suction chamber 7a ″, and the second suction chamber 7b ″. When the compressor 1 ″ expands, pressure pulsation generated during the middle rotation operation is reduced, and the flow rate is increased when the refrigerant passes through the communication passage 13a ″ and the communication passage 13 ″ having a predetermined cross-sectional area. Pressure pulsation that occurs when the compressor 1 ″ operates at a low speed is reduced.

  As a result, the generation of abnormal noise can be reduced in a wide range from the low rotation range to the middle rotation range of the compressor 1 ″ that is particularly worrisome for the occupant, and a reduction in suction efficiency can be prevented.

  The total cross-sectional area of the communication passage 13 ″ is larger than the cross-sectional area of the choke portion formed by the suction hole 11 ″ in the suction stroke and the suction-side reed valve 14 provided in the valve plate 9. Since the communication path 13 ″ is formed, it is possible to reduce the occurrence of abnormal noise in the low rotation range without the communication path 13 ″ becoming a suction resistance.

  The suction chamber 7 ″ having an internal volume necessary for reducing pressure pulsation can be formed without increasing the size of the entire apparatus in the radial direction.

  Since each of the suction chamber 7 "and the discharge chamber 8" is formed of separate members, the manufacturing process of the rear housing 6 "is simplified, and the manufacturing cost can be reduced.

  Since the first suction chamber 7 a ″, the second suction chamber 7 b ″, and the muffler chamber 18 ″ have different internal volumes, the frequency range of pressure pulsation that can be eliminated can be changed. Generation of abnormal noise in the area can be reduced.

It is a whole sectional view of the compressor concerning this embodiment. It is sectional drawing of 1st Embodiment along the AA line of FIG. It is sectional drawing along the surface similar to FIG. 1 about the rear housing of 2nd Embodiment. It is sectional drawing along the surface similar to FIG. 1 about the rear housing of 3rd Embodiment. It is sectional drawing along the AA of FIG. 1 about the rear housing of another aspect of 1st Embodiment. It is sectional drawing along the surface similar to FIG. 1 about the rear housing of 1st Embodiment.

Explanation of symbols

1 ... Variable capacity compressor (compressor)
2 ... Cylinder block 3 ... Cylinder bore 4 ... Front housing 5 ... Crank chamber 6 ... Rear housing 7 ... Suction chamber 7a ... First suction chamber 7b ... Second suction chamber 8 ... Discharge chamber 9 ... Valve plate 10 ... Bulkhead 11 ... Suction hole 13 ... Communication passage 14 ... Suction side reed valve (valve mechanism)
16 ... Suction port 29 ... Piston S ... Drive shaft

Claims (7)

A front housing (4) is joined to a front end face of a cylinder block (2) having a cylinder bore (3) to form a crank chamber (5), and a valve plate (9) is attached to a rear end face of the cylinder block (2). ) To join the rear housing (6) to form the suction chamber (7) and the discharge chamber (8), utilizing the rotation of the drive shaft (S) supported in the crank chamber (5). In the compressor for reciprocating the piston (29),
The suction chamber (7) is in communication with a first suction chamber (7a) connected to a suction port (16) to which a refrigerant is supplied from the outside, and a second suction port is connected to the cylinder bore (3) through the valve plate. The suction chamber (7b), and the first suction chamber (7a) and the second suction chamber (7b) are divided by the partition wall (10), and at least 2 formed in the partition wall (10). A compressor characterized in that it is communicated by at least one communication passage (13). The compressor according to claim 1,
The compressor characterized in that one of the communication passages (13) is formed in the partition wall (10) located in front of the outlet of the suction port (16). In the compressor according to claim 1 or 2,
A choke portion formed by the suction hole (11) in the suction stroke in the suction hole (11) provided in the valve plate (9) and the valve mechanism (14) provided in the valve plate (9). The compressor is characterized in that the communication passage (13) is formed such that the total cross-sectional area of the communication passage (13) is larger than the passage cross-sectional area of the communication passage (13). In the compressor given in any 1 paragraph of Claims 1-3,
The second suction chamber (7b) having a substantially ring shape is provided on the outer peripheral portion of the circumferential portion of the first suction chamber (7a) having a substantially cylindrical shape with the partition wall (10) interposed therebetween,
The discharge chamber (8) having a substantially cylindrical shape is formed between the first suction chamber (7a) and the valve plate (9) and in the inner peripheral portion of the second suction chamber (7b). Features compressor. The compressor according to claim 4, wherein
The compressor characterized in that each of the suction chamber (7) and the discharge chamber (8) constituting the rear housing (6) is formed of a separate member. In the compressor given in any 1 paragraph of Claims 1-5,
The compressor characterized in that the first suction chamber (7a) and the second suction chamber (7b) have different internal volumes. In the compressor given in any 1 paragraph of Claims 1-6,
At least a portion of the partition wall (10) has a wall surface forming a suction port passage (16a) communicating the suction port (16) and the suction chamber (7);
A compressor characterized in that it is formed by a wall surface that forms a discharge port passage (17a) that communicates the discharge port (17) and the discharge chamber (8).

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