JP5783354B2 - Compressor - Google Patents

Description

  The present invention relates to a technique for reducing the level of noise caused by refrigerant pressure pulsation in a compressor used in a refrigeration cycle air conditioner or the like.

  In Patent Document 1, a cylinder block having a plurality of cylinder bores that are arranged around a drive shaft and in which a piston is reciprocally inserted, and joined to an end face of the cylinder block and communicated with each cylinder bore via a suction valve mechanism. There is disclosed a compressor that includes a suction chamber and a cylinder head having a discharge chamber that communicates with each cylinder bore via a discharge valve mechanism, and the discharge chamber is formed around the outside of the suction chamber.

  In order to reduce the pressure pulsation that causes noise and noise, the discharge chamber is divided into a plurality of small chambers in the circumferential direction by a plurality of ribs, and the small chambers are separated from each other by a protruding end of the rib and a valve plate (suction valve mechanism, discharge valve mechanism). And a communication passage through a throttle passage formed between the two.

  As a result, the high-pressure refrigerant discharged from the cylinder bore expands in the small chamber, passes through the throttle passage, contracts, and expands again in the adjacent small chamber. Out of the machine to the external refrigeration circuit.

Japanese Patent Laid-Open No. 7-233783

  However, in the configuration of Patent Document 1, since the sound wave makes one round in the cylinder head through the throttle passage formed along the valve plate surface between the rib and the valve plate, the natural frequency of the compressor The resonance in the vicinity could not be sufficiently reduced, and the noise level was deteriorated.

  The present invention has been made paying attention to such a conventional problem, and an object thereof is to sufficiently reduce a noise level by reducing resonance caused by pressure pulsation of a compressor.

For this reason, the present invention
A cylinder block having a plurality of cylinder bores that are arranged around the drive shaft and in which pistons are reciprocally inserted; and a valve plate that is joined to the end face of the cylinder block and includes intake and discharge valves that communicate with each cylinder bore; A suction chamber that is connected to the valve plate and communicates with each cylinder bore via a suction valve, and a cylinder head that has a discharge chamber that communicates with each cylinder bore via a discharge valve, and one of the suction chamber and the discharge chamber is the other The compressor formed around the outside of the compressor has the following configuration.

A plurality of ribs that divide the suction chamber or discharge chamber formed around the outside into a plurality of small chambers in the circumferential direction are disposed, and a communication passage that communicates the small chambers adjacent to each rib is disposed. At least one of the plurality of communication passages is a communication hole formed in the rib, and the position in the drive shaft direction is different from other communication passages so as to change the flow direction of the refrigerant in a wave shape, or The positions of the plurality of communication paths in the drive shaft direction are different at least at one place so that the paths do not overlap each other.

  Since the positions of the plurality of communication paths in the drive axis direction are different at least at one location, the sound wave that has passed through a certain communication path is reflected by a rib formed with a communication path that is different in position in the drive axis direction from the communication path. Therefore, it is avoided that the sound wave makes one round in the cylinder head, the resonance is effectively suppressed, and the noise level can be sufficiently reduced.

The longitudinal section showing the variable capacity compressor which provided the valve device concerning the present invention. The cross-sectional view of the cylinder head of a compressor same as the above. The figure which shows 1st Embodiment which made the height of the communicating hole formed in the rib of a cylinder head same as the above differ with a function. The figure which similarly shows 2nd Embodiment. The figure which similarly shows 3rd Embodiment. The diagram which shows the noise level reduction effect by this invention. The diagram which shows the effect | action which can maintain a refrigerant | coolant flow volume in this invention. The perspective view which shows another form of the communicating hole formation of a rib. The figure which shows embodiment using the communicating hole formed with another form same as the above.

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
FIG. 1 shows a compressor according to an embodiment, and this compressor is a swash plate type variable capacity reciprocating compressor 100 used in a vehicle air conditioner system.

  The compressor 100 includes a cylinder block 101, a front housing 102 connected to one end of the cylinder block 101, and a cylinder head 104 connected to the other end of the cylinder block 101 via a valve plate 103.

  A crank chamber 105 is defined by the cylinder block 101 and the front housing 102, and the drive shaft 106 has radial and thrust bearings 113 with respect to the cylinder block 101 and the front housing 102 so as to cross the crank chamber 105. , 115 and 116 are rotatably supported.

The front end portion of the drive shaft 106 penetrates through the boss portion 102a of the front housing 102 and protrudes to the outside of the front housing 102. A drive source such as a vehicle engine or motor is connected to the front end portion protruding outside the power transmission device. It is connected via.
A shaft seal device 112 is provided between the drive shaft 106 and the boss portion 102a to block the inside of the front housing 102 (crank chamber 105) from the outside.

In the crank chamber 105, a rotor 108 is fixed to the drive shaft 106, and a swash plate 107 is attached to the rotor 108 via a connecting portion 109.
The swash plate 107 is supported so that the drive shaft 106 passes through a through-hole formed in the center of the swash plate 107, rotates integrally with the drive shaft 106, and is slidable and tiltable in the axial direction of the drive shaft 106. . Further, the rotor 108 is rotatably supported by a thrust bearing 114 disposed on the front end side inner wall of the front housing 102.

  Between the rotor 108 and the swash plate 107, a coil spring 110 that urges the swash plate 107 in a direction to reduce the inclination angle of the swash plate 107 is mounted, and between the cylinder block 101 and the swash plate 107. Is mounted with a coil spring 111 for urging the swash plate 107 in a direction to increase the inclination angle of the swash plate 107.

  A plurality of cylinder bores 101 a are formed in the cylinder block 101 so as to surround the drive shaft 106, and a piston 117 is accommodated in each cylinder bore 101 a so as to be capable of reciprocating in the axial direction of the drive shaft 106. Each piston 117 is engaged with the outer peripheral portion of the swash plate 107 via a shoe 118. When the swash plate 107 rotates together with the drive shaft 106, each piston 117 reciprocates in the cylinder bore 101a.

  The cylinder head 104 is provided with a suction chamber 119 on an extension line of the drive shaft 106 and a discharge chamber 120 that surrounds the suction chamber 119 in an annular shape. The suction chamber 119 communicates with the cylinder bore 101a through a communication hole 103a provided in the valve plate 103 and a valve body 150a of the suction valve, and the discharge chamber 120 communicates with a communication hole provided in the valve body 150b of the discharge valve and the valve plate 103. It communicates with the cylinder bore 101a via 103b.

  The front housing 102, the cylinder block 101, the valve plate 103, and the cylinder head 104 are fastened by a plurality of through bolts 140 via a gasket (not shown) to form a compressor housing.

  A muffler 121 is provided outside the cylinder block 101. In the muffler 121, a communication passage 121a communicating with the discharge chamber 120 is formed by overlapping with a communication passage 103c formed in the valve plate, and a check valve 200 is incorporated. The check valve 200 is opened only when the pressure in the upstream discharge chamber 120 is higher than the downstream pressure by a predetermined amount or more, and the refrigerant flowing from the discharge chamber 120 through the communication passages 103c and 121a is discharged from the discharge port 121b. It is designed to be discharged.

  The cylinder head 104 is formed with a suction port 104a connected to a suction side refrigerant circuit (evaporator) of the vehicle air conditioner system, and an opening adjusting valve 250 is interposed in the vicinity of the downstream side of the suction port 104a. The refrigerant whose flow rate is adjusted from the side refrigerant circuit (evaporator) through the suction port 104 a and the opening degree adjustment valve 250 is sucked into the suction chamber 119.

A capacity control valve 300 is attached to the cylinder head 104.
The capacity control valve 300 adjusts the opening degree of the communication passage 125 that communicates the discharge chamber 120 and the crank chamber 105, and controls the amount of refrigerant discharged into the crank chamber 105.

  In addition, the refrigerant in the crank chamber 105 passes through the gaps between the bearings 115 and 116 and the drive shaft 106 and enters the suction chamber 119 via the space 127 formed in the cylinder block 101 and the orifice 103 d formed in the valve plate 103. Inflow.

  Therefore, the displacement control valve 300 adjusts the amount of refrigerant introduced into the crank chamber 105 to change the pressure of the crank chamber 105, and the inclination angle of the swash plate 107, that is, the stroke amount of the piston 117 is changed. The discharge capacity of the machine 100 can be controlled.

  The capacity control valve 300 adjusts the energization amount to the built-in solenoid based on the external signal, and the pressure of the suction chamber 119 introduced into the pressure sensing chamber of the capacity control valve 300 via the communication path 126 is a predetermined value. The discharge capacity of the compressor 100 is controlled so that the communication path 125 is forcibly opened by shutting off the power supply to the built-in solenoid, and the discharge capacity of the compressor 100 is controlled to the minimum.

Next, in order to reduce the level of noise due to pressure pulsation, the configuration disposed in the discharge chamber 120 will be described.
As shown in FIG. 2, a plurality of ribs 151 are arranged between the outer peripheral wall 104 b of the cylinder head 104 and the inner peripheral wall 104 c partitioning the suction chamber 119 and the discharge chamber 120 in the radial direction of a circle centering on the drive shaft 106. And the inside of the discharge chamber 120 is partitioned into small chambers 120a to 120g communicated one by one with the communication hole 103b on the discharge side of each cylinder bore 101a. Among these, one small chamber (for example, the small chamber 120 a) communicates with the communication path 103 c of the valve plate 103.

  In addition, a plurality of communication holes (communication paths) 151a to 151g that allow the small chambers 120a to 120g to communicate with each rib 151 are arranged at positions in the axial direction of the drive shaft 106 (height position from the end wall of the cylinder head 104, hereinafter referred to as communication holes). (Referred to as “height of”).

3 to 5 show various embodiments in which at least one height of the communication holes 151a to 151g is changed in a state where the small chambers 120a to 120g are linearly developed.
In the embodiment of FIGS. 3 and 4, the heights of the communication holes 151 a to 151 g are made different every other in the circumferential direction. The sound wave that has passed through any of the communication holes 151a to 151g hits and reflects the wall surface of the rib 151 adjacent to the communication hole. In this way, it is possible to prevent the sound wave from making a round around the cylinder head 104.

  For this reason, as shown in FIG. 6, the resonance in the vicinity of the natural frequency of the compressor 100 (for example, around 400 to 500 Hz) can be effectively suppressed, and the noise level can be sufficiently reduced.

By the way, since the flow direction of the refrigerant changes in a wave shape by changing the height of the communication hole, an increase in flow resistance can be considered.
However, in the present invention, since the noise level can be greatly reduced by increasing the resonance suppression effect, the noise level can be reduced by reducing the opening area of the communication path as in Patent Document 1 and repeatedly performing expansion, contraction, and contraction. No function is required or the share of the function can be reduced. Therefore, since the flow area of the refrigerant can be reduced by increasing the opening area of the communication hole, the compression is reduced even when compared with the case where the communication path having the same height and the small opening area is provided as in Patent Document 1. It is also possible to increase the efficiency of the machine (coefficient of performance COP) to the same level or higher.

  Incidentally, if the total opening area of the communication holes is greater than or equal to a predetermined value, the total opening area of the communication holes is the same, the same height, and the same operating conditions (same discharge pressure, same suction pressure) as shown in FIG. As a result, it was confirmed that the refrigerant flow rates can be maintained substantially the same.

On the other hand, it is also possible to further improve the noise level function by reducing the opening area of the communication hole and using the noise level reduction function by repeated expansion and contraction.
However, if the opening area of the communication hole is reduced, an increase in flow resistance due to the change in the flow direction of the refrigerant by changing the height of the communication hole cannot be ignored, and the flow rate of the refrigerant is affected. Conceivable.

  Therefore, when the opening area of the communication hole is made smaller than a predetermined value, the communication holes 151a and 151b immediately upstream adjacent to the refrigerant outlet (the communication path 103c of the valve plate 103) as shown in FIG. It is preferable to approach the height of the refrigerant outlet because the change in the refrigerant flow direction becomes smaller and the flow resistance can be reduced.

  Further, as shown in FIG. 5, if the communication holes 151a, 151b, 151c, 151g from the refrigerant outlet to the second upstream side are made closer to the height of the refrigerant outlet, the flow resistance can be further reduced.

  Moreover, you may form the communicating hole formed in the rib 151 in a diagonal direction, as shown in FIG. When the rib 151 is integrally formed on the cylinder head 104 by casting or the like, it is difficult to process the communication hole parallel to the thickness direction of the rib 151. However, if the processing is performed obliquely, the cylinder head 104 is set obliquely. Can be easily processed. In particular, since there is a portion to be processed in a state where the cylinder head 104 is set obliquely other than the communication hole of the rib 151, it can be processed efficiently at the same time.

  Further, when the communication holes are formed in an oblique direction, as shown in FIG. 9, the communication holes 151a and 151b immediately upstream of the refrigerant outlet are set to have a hole axis in the direction in which the refrigerant is directed to the refrigerant outlet. The flow resistance can be further reduced by setting the hole axis so that the communication hole also follows the flow direction of the refrigerant.

  On the other hand, the rib 151 can be formed of a member separate from the cylinder head 104 in addition to the one integrally formed with the cylinder head 104 as in the above embodiment. In this case, the rib 151 can be formed of a resin having durability against the temperature state during the compressor operation, and the weight of the compressor can be reduced.

The present invention is not limited to the embodiment described above.
For example, in the above embodiment, the present invention is applied to a compressor having a suction chamber on the center side of the cylinder head and having a discharge chamber outside the suction chamber, but has a discharge chamber on the center side of the cylinder head, There is also a compressor having a suction chamber outside the discharge chamber. In this case, the present invention can be similarly applied to the outer suction chamber, and the noise level due to the intake pulsation can be reduced.

  Further, as in the above embodiment, the outer discharge chamber or suction chamber may be partitioned into small chambers having a number smaller than the number of cylinder bores. Therefore, the number of ribs may be two or more, and it is sufficient that at least one of the communication holes formed in the two or more ribs has a different height.

  Moreover, the cross-sectional shape and cross-sectional area of the communication hole formed in each rib may differ, and a plurality of communication holes may be formed for each rib. Further, when the hole axis of the communication hole is formed in an oblique direction, the direction of the hole axis of each communication hole may be different, and a plurality of communication holes may be arranged to intersect with one rib. .

The small chambers partitioned by the ribs and the valve plate surface may be completely sealed, but may have a gap that can substantially block sound waves.
Further, among the communication holes formed in the plurality of ribs, the heights are different even if the communication holes formed between the concave grooves formed at the protruding ends of the ribs on the valve plate side and the valve plate surface are included. What is necessary is just to have another communicating hole.

DESCRIPTION OF SYMBOLS 100 ... Compressor 101 ... Cylinder block 101a ... Cylinder bore 103 ... Valve plate 103a ... Communication hole (suction side) of valve plate
103b ... Valve plate communication hole (discharge side)
103c ... Valve plate communication passage (refrigerant outlet)
DESCRIPTION OF SYMBOLS 104 ... Cylinder head 104b ... Cylinder head outer peripheral wall 104c ... Cylinder head inner peripheral wall 106 ... Drive shaft 119 ... Suction chamber 120 ... Discharge chamber 120a-120g ... Small chamber 151 ... Rib 151a-151g ... Rib communication hole

Claims (6)

A cylinder block having a plurality of cylinder bores that are arranged around a drive shaft and in which pistons are reciprocally inserted, and a valve plate that is joined to an end surface of the cylinder block and communicates with the cylinder bores. And a suction chamber that is connected to the valve plate and communicates with each of the cylinder bores via the suction valve, and a cylinder head having a discharge chamber that communicates with each of the cylinder bores via the discharge valve. And a compressor in which one of the discharge chambers is formed around the other outer side,
A plurality of ribs that divide the suction chamber or the discharge chamber formed around the outside into a plurality of small chambers in the circumferential direction, and a communication passage that communicates the small chambers adjacent to the ribs; At least one of the plurality of communication passages is a communication hole formed in the rib, and the position in the drive shaft direction is different from the other communication passages so as to change the flow direction of the refrigerant in a wave shape. Features compressor. A cylinder block having a plurality of cylinder bores that are arranged around a drive shaft and in which pistons are reciprocally inserted, and a valve plate that is joined to an end surface of the cylinder block and communicates with the cylinder bores. And a suction chamber that is connected to the valve plate and communicates with each of the cylinder bores via the suction valve, and a cylinder head having a discharge chamber that communicates with each of the cylinder bores via the discharge valve. And a compressor in which one of the discharge chambers is formed around the other outer side,
A plurality of ribs that divide the suction chamber or the discharge chamber formed around the outside into a plurality of small chambers in the circumferential direction, and a communication passage that communicates the small chambers adjacent to the ribs; In addition, the compressor is characterized in that the positions of the plurality of communication paths in the drive shaft direction are different at least at one place so that the communication paths do not overlap each other . The compressor according to claim 1 or 2 , wherein the communication path is formed by a hole penetrating the rib in an oblique direction. When a discharge chamber is formed around the outer periphery, a discharge port of the discharge chamber is formed in the peripheral wall of the cylinder head, and the vicinity of the extension line of the hole axis of the communication path formed in a rib adjacent to the discharge port The compressor according to any one of claims 1 to 3 , further comprising the discharge port. When a suction chamber is formed around the outer periphery, a suction port of the suction chamber is formed in the peripheral wall of the cylinder head, and the vicinity of the extension line of the hole axis of the communication path formed in a rib adjacent to the suction port The compressor according to any one of claims 1 to 3 , further comprising the suction port. The compressor according to any one of claims 1 to 5 , wherein the rib is formed of a member separate from the cylinder head.

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