JP2018150917A - Swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a swash plate compressor capable of easily reducing discharge pulsation of a given frequency.SOLUTION: In a swash plate compressor, a pulsation reduction flow passage 37 and a regulation wall 3d are formed in a rear housing 3. The pulsation reduction flow passage 37 can circulate refrigerant in a discharge chamber 3a therein, and a communication port 37a of its one end is opened toward the discharge chamber 3a, while the other end thereof is closed by a partition wall 36. The regulation wall 3d is arranged between adjacent cylinder bores 1a and sections the discharge chamber 3a to regulate refrigerant in the discharge chamber 3a in a circulation direction.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a swash plate compressor.

  A typical swash plate compressor includes a cylinder block, a housing, a drive shaft, a swash plate, and a plurality of pistons. A plurality of cylinder bores are formed in the cylinder block. The housing is joined to the cylinder block. A swash plate chamber and a discharge chamber capable of communicating with each cylinder bore are formed inside the housing. The drive shaft is rotatably supported on the housing. The swash plate is disposed in the swash plate chamber and is rotated together with the drive shaft. Each piston is housed in a cylinder bore, reciprocates in the cylinder bore by the rotation of the swash plate, and forms a compression chamber in the cylinder bore. Such a swash plate compressor has a problem that the pulsation in the discharge chamber resonates and the discharge pulsation increases. It is known that the resonance frequency varies depending on the rotational speed of the drive shaft, the discharge pressure of the refrigerant, and the like.

  For this reason, the compressor of patent document 1 is proposed. In this compressor, a resonance chamber to which a damping action of a Helmholtz resonator is applied is provided in a housing, and this resonance chamber communicates with the discharge chamber. In this compressor, the resonance chamber attenuates the pulsation of a specific frequency by the resonance chamber, and the discharge pulsation can be reduced.

JP 2000-161219 A

  However, Helmholtz resonators can only reduce relatively high frequency pulsations.

  The present invention has been made in view of the above-described conventional situation, and an object to be solved is to provide a swash plate compressor that can easily reduce discharge pulsation of an arbitrary frequency.

The swash plate compressor of the present invention includes a cylinder block in which a plurality of cylinder bores are formed,
A housing which is joined to the cylinder block, and in which a swash plate chamber and a discharge chamber capable of communicating with each cylinder bore are formed;
A drive shaft rotatably supported on the housing;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
In a swash plate type compressor having a piston housed in each cylinder bore and reciprocating in each cylinder bore by rotation of the swash plate and forming a compression chamber in each cylinder bore,
In the housing, the refrigerant in the discharge chamber can flow therethrough, the communication port at one end is opened toward the discharge chamber, and the pulsation reducing flow path is closed at the other end, and between the adjacent cylinder bores. It is arranged to partition the discharge chamber and to form one regulating wall for regulating the flow direction of the refrigerant in the discharge chamber.

  In the compressor of the present invention, the pulsation reducing flow path through which the refrigerant in the discharge chamber can flow is opened at one end toward the discharge chamber and closed at the other end. In addition, a regulating wall is disposed between adjacent cylinder bores to partition the discharge chamber, and the flow direction of the refrigerant in the discharge chamber is regulated by the regulating wall. In other words, in this compressor, the pulsation reducing flow path becomes a so-called side branch that can reduce pulsation of a specific frequency, and the pulsation in the discharge chamber is attenuated by interfering with the pulsation propagating through the side branch, thereby reducing the discharge pulsation. it can. This side branch can arbitrarily select the specific frequency of the pulsation to be reduced only by changing the length.

  Therefore, in the compressor of the present invention, discharge pulsation at an arbitrary frequency can be easily reduced.

  In addition, since the pulsation reducing flow path constituting the side branch is easier to manufacture than the resonance chamber to which the damping action of the Helmholtz resonator is applied, this compressor realizes a reduction in manufacturing cost by simplifying the structure. You can also.

  The discharge chamber is preferably formed in an annular shape. The housing has a suction chamber formed inside the discharge chamber and capable of communicating with each cylinder bore, and a partition wall that is located between the suction chamber and the discharge chamber and separates the suction chamber and the discharge chamber. Is preferred. And it is preferable that the pulsation reduction flow path is formed in the partition. In this case, the pulsation reducing flow path can be easily manufactured in the housing.

  A gasket may be provided between the discharge chamber and the cylinder block. The pulsation reducing flow path is preferably partitioned within the discharge chamber by a partition wall and a gasket. In this case, it is easy to configure a long pulsation reducing flow path, and it is possible to reliably realize a reduction in manufacturing cost.

  The discharge chamber can communicate with each compression chamber by a discharge port. The housing may have an outlet that opens into the discharge chamber adjacent to the communication port, and a discharge passage that guides the refrigerant in the discharge chamber to the outside of the discharge chamber. It is preferable that the communication port and the outflow port are arranged on the downstream side in the flow direction of the refrigerant in the discharge chamber with respect to all the discharge ports. In this case, the refrigerant compressed in each compression chamber can be circulated in one direction to the outlet, and an interference action by the pulsation reducing flow path can be imparted to the downstream refrigerant flowing in this way, so that the discharge pulsation is effective. Can be reduced.

  In the compressor of the present invention, discharge pulsation at an arbitrary frequency can be easily reduced.

It is sectional drawing of the capacity | capacitance variable type swash plate type compressor of an Example. 1 is a plan view of a rear housing according to a variable capacity swash plate compressor of an embodiment.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings.

  As shown in FIG. 1, the compressor of the embodiment is a variable displacement swash plate compressor having a discharge chamber 3a only on one side. In this compressor, as shown in FIG. 2, a plurality of cylinder bores 1 a are penetrated through the cylinder block 1 at equiangular intervals concentrically around the drive shaft center of the drive shaft 13. As shown in FIG. 1, a valve unit 5 is provided between the rear end of the cylinder block 1 and the front end of the rear housing 3, and a front housing 7 is provided at the front end of the cylinder block 1. 9 is fastened. This compressor is fixed to a vehicle engine (not shown).

  As shown in FIG. 2, the rear housing 3 is formed with an annular discharge chamber 3a and a suction chamber 3b located inside the discharge chamber 3a. The discharge chamber 3 a and the suction chamber 3 b are partitioned by a partition wall 36. As shown in FIG. 1, the valve unit 5 is formed with a plurality of discharge ports 5a and the same number of suction ports 5b as the discharge ports 5a. The discharge chambers 3a communicate with the cylinder bores 1a by the discharge ports 5a. The suction chamber 3b communicates with each cylinder bore 1a through each suction port 5b.

  A crank chamber 11 is formed in the front housing 7. The crank chamber 11 corresponds to a swash plate chamber. Further, a shaft hole 7a is provided in the front housing 7 so as to communicate with the outside and the crank chamber 11, and a drive shaft 13 is inserted into the shaft hole 7a. A shaft seal device 15 and a first radial bearing 17 are provided between the shaft hole 7 a and the drive shaft 13. The drive shaft 13 is belt-driven by a vehicle engine.

  A lug plate 19 is press-fitted into the drive shaft 13 in the crank chamber 11. A thrust bearing 21 is provided between the lug plate 19 and the front housing 7. A swash plate 23 is provided in the crank chamber 11, and the drive shaft 13 is inserted through the swash plate 23. A link mechanism 25 is provided between the lug plate 19 and the swash plate 23 so that the swash plate 23 can change the inclination angle while the lug plate 19 transmits the rotational driving force of the drive shaft 13. A shaft hole 1b is also formed in the cylinder block 1, and the rear end of the drive shaft 13 is located in the shaft hole 1b. A second radial bearing 27 is provided between the drive shaft 13 and the shaft hole 1b.

  Each cylinder bore 1a accommodates a single-headed piston 29 so as to be able to reciprocate. Between the swash plate 23 and each piston 29, shoes 31a and 31b are provided that make a pair in front and rear. In each cylinder bore 1a, a compression chamber 33 is defined by the valve unit 5 and each piston 29. The lug plate 19, the link mechanism 25, the swash plate 23, the shoes 31 a and 31 b, the pistons 29, and the valve unit 5 correspond to the compression mechanism 6.

  Although not shown, the rear housing 3 is provided with a capacity control valve. The discharge chamber 3a and the capacity control valve are in communication with each other through the first air supply passage, and the capacity control valve and the crank chamber 11 are in communication with each other through the second air supply passage. The suction chamber 3b and the crank chamber 11 are communicated with each other through an extraction passage. The capacity control valve adjusts the pressure in the crank chamber 11 by the pressure in the suction chamber 3b or the like. Thereby, the inclination angle of the swash plate 11 is changed.

  In this compressor, when the drive shaft 13 is rotationally driven by the vehicle engine, the lug plate 19 and the swash plate 23 rotate in the crank chamber 11, and each piston 29 reciprocates in the cylinder bore 1a. Therefore, each piston 29 reciprocates in the cylinder bore 1a with a stroke corresponding to the inclination angle of the swash plate 23. Therefore, the refrigerant in the suction chamber 3b is sucked into the compression chamber 33, the refrigerant is compressed in the compression chamber 33, and the high-pressure refrigerant is discharged from the compression chamber 33 to the discharge chamber 3a.

  In the meantime, in this compressor, the pressure in the crank chamber 11 is adjusted by the capacity control valve, and the discharge capacity can be changed as appropriate. For example, if the capacity control valve increases the communication area between the first supply passage and the second supply passage, the refrigerant having the discharge pressure in the discharge chamber 3a can easily flow into the crank chamber 11, and the crank chamber pressure is reduced. Get higher. In this case, the inclination angle of the swash plate 23 is reduced, and the discharge capacity per rotation of the drive shaft 13 is reduced. Further, if the capacity control valve reduces the communication area between the first supply passage and the second supply passage, the refrigerant having the discharge pressure is less likely to flow into the crank chamber 11. For this reason, the refrigerant in the crank chamber 11 easily flows out to the suction chamber 3b through the extraction passage, and the crank chamber pressure is lowered. In this case, the inclination angle of the swash plate 23 increases and the discharge capacity increases.

  As shown in FIGS. 1 and 2, the rear housing 3 is formed with a discharge passage 35 communicating with the discharge chamber 3a and the outlet 3c. The discharge passage 35 is opened to the outside by a discharge port 35a. Further, as shown in FIG. 2, a pulsation reducing flow path 37 is formed in the rear housing 3. The pulsation reducing flow path 37 is formed by recessing the partition wall 36. The pulsation reducing flow path 37 has a communication port 37 a at one end opened toward the discharge chamber 3 a and the other end closed by a partition wall 36. The refrigerant in the discharge chamber 3a can flow through the pulsation reducing flow path 37 through the communication port 37a.

  Further, the rear housing 3 is formed with a regulating wall 3d that is disposed between the adjacent discharge ports 5a and partitions the discharge chamber 3a. The restriction wall 3d divides the annular discharge chamber 3a and restricts the flow direction of the refrigerant in the discharge chamber 3a so that the refrigerant in the discharge chamber 3a flows in one direction and reaches the communication port 37a. The communication port 37a of the pulsation reducing flow path 37 is adjacent to the restriction wall 3d, and the outlet 3c of the discharge passage 35 is also adjacent to the restriction wall 3d. That is, the communication port 37a and the outflow port 3c are arranged downstream of all the discharge ports 5a in the flow direction of the refrigerant in the discharge chamber 3a.

  The valve unit 5 has a retainer plate 5c on the rear housing 3 side. Rubber gaskets are integrally formed on the front and rear surfaces of the retainer plate 5c. A discharge valve plate, a valve plate, and a suction valve plate are located in front of the retainer plate 5c. The retainer plate 5c regulates the lift amount of each discharge reed valve in the discharge valve plate. The pulsation reducing flow path 37 is partitioned in the discharge chamber 3a by the partition wall 36 and the retainer plate 5c. That is, the pulsation reducing flow path 37 is partitioned in the discharge chamber 3a by the partition wall 36 and the gasket.

  As shown in FIG. 1, a suction passage 51 that opens to the outside is formed in the suction chamber 3b. An evaporator is connected to the suction passage 51 through a pipe line. On the other hand, a condenser is connected to the discharge port 35a of the discharge passage 35 by a pipe line. An expansion valve is provided between the evaporator and the condenser. The compressor, the evaporator, the condenser, the expansion valve, and the pipe line connecting them constitute a refrigeration circuit.

  In this compressor, the communication port 37a of the pulsation reducing flow path 37 is opened in the discharge chamber 3a, the regulating wall 3d defines the discharge chamber 3a, and the refrigerant in the discharge chamber 3a is communicated while flowing in one direction. The flow direction of the refrigerant in the discharge chamber 3a is regulated so as to reach the port 37a. That is, in this compressor, the pulsation reducing flow path 37 is a so-called side branch. The side branch is provided in the main pipeline and reduces pulsation at a specific frequency due to interference of the side branch. The specific frequency in the refrigerant introduced from the main pipe to the side branch returns to the branch point with a half-wave phase delay in the reciprocation of the side branch, and is synthesized with the opposite phase to the specific frequency in the main pipe to reduce pulsation. To do. Thus, in this compressor, discharge pulsation can be reduced. The side branch composed of the pulsation reducing flow path 37 can arbitrarily select a specific frequency of pulsation to be reduced only by changing the length.

  Therefore, in this compressor, the discharge pulsation of an arbitrary frequency can be easily reduced.

  Further, in this compressor, since the pulsation reducing flow path 37 constituting the side branch is easier to manufacture than the resonance chamber to which the damping action of the Helmholtz resonator is applied, the manufacturing cost can be reduced by simplifying the structure. You can also. In particular, in this compressor, since the pulsation reducing flow path 37 is partitioned from the discharge chamber 3a by the partition wall 36 and the retainer plate 5c, the long pulsation reducing flow path 37 can be easily formed, and the manufacturing cost can be reduced. It can be realized reliably.

  Moreover, in this compressor, since the communication port 37a and the outflow port 3c are arrange | positioned in the downstream of the distribution direction of a refrigerant | coolant, the refrigerant | coolant compressed by each compression chamber 33 can be distribute | circulated to the outflow port 3c by one direction. At the same time, since the interference action by the pulsation reducing flow path 37 can be provided on the downstream side of the circulating refrigerant, the discharge pulsation can be effectively reduced.

  While the present invention has been described with reference to the embodiments, it is needless to say that the present invention is not limited to the above-described embodiments and can be appropriately modified and applied without departing from the spirit thereof.

  For example, the compressor is not limited to a type that adjusts the pressure of the crank chamber 11 to change the inclination angle of the swash plate 11 and changes the discharge capacity, as in the embodiment, and uses an actuator to adjust the swash plate. It may be of a type that changes the inclination angle. Further, the compressor may be a variable capacity type that can change the inclination angle of the swash plate, or may be a fixed capacity type that cannot change the inclination angle of the swash plate.

  Further, in the above embodiment, the entire pulsation reducing flow path 37 is located in the rear housing 3, but the pulsation reducing flow path 37 only needs to have a communication port 37a opened in the discharge chamber 3a. It does not have to be located in the rear housing 3.

  Furthermore, the number of pulsation reduction channels 37 is not limited to one, and may be two or more.

  Moreover, in the said Example, although the control wall 3d is arrange | positioned in the position adjacent to the communication port 37a of the pulsation reduction flow path 37, and the outflow port 3c of the discharge channel 35, the control wall 3d is the communication port 37a and the outflow port 3c. You may arrange | position in the position away from. That is, the regulation wall 3d only needs to be disposed between any adjacent discharge ports 5a. Accordingly, the regulation wall 3d may reach the communication port 37a while circulating the refrigerant in the discharge chamber 3a in two directions.

  Furthermore, the gasket may not be integral with the retainer plate.

  The present invention is applicable to a vehicle air conditioner.

DESCRIPTION OF SYMBOLS 1a ... Cylinder bore 1 ... Cylinder block 3a ... Discharge chamber 11 ... Swash plate chamber (crank chamber)
3, 7 ... Housing (3 ... Rear housing, 7 ... Front housing)
DESCRIPTION OF SYMBOLS 13 ... Drive shaft 23 ... Swash plate 33 ... Compression chamber 29 ... Piston 5a ... Discharge port 37a ... Communication port 37 ... Pulsation reduction flow path 3d ... Restriction wall 3b ... Suction chamber 36 ... Septum 5c ... Gasket (retainer plate)
3c ... Outlet 35 ... Discharge passage

Claims (4)

A cylinder block formed with a plurality of cylinder bores;
A housing which is joined to the cylinder block, and in which a swash plate chamber and a discharge chamber capable of communicating with each cylinder bore are formed;
A drive shaft rotatably supported on the housing;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
In a swash plate type compressor having a piston housed in each cylinder bore and reciprocating in each cylinder bore by rotation of the swash plate and forming a compression chamber in each cylinder bore,
In the housing, the refrigerant in the discharge chamber can flow therethrough, the communication port at one end is opened toward the discharge chamber, and the pulsation reducing flow path is closed at the other end, and between the adjacent cylinder bores. A swash plate compressor characterized in that it is disposed to partition the discharge chamber and to form one restricting wall for restricting the flow direction of the refrigerant in the discharge chamber. The discharge chamber is formed in an annular shape,
The housing includes a suction chamber formed inside the discharge chamber and capable of communicating with each cylinder bore, and a partition wall that is located between the suction chamber and the discharge chamber and separates the suction chamber and the discharge chamber. And formed,
The swash plate compressor according to claim 1, wherein the pulsation reducing flow path is formed in the partition wall. A gasket is provided between the discharge chamber and the cylinder block,
The swash plate compressor according to claim 2, wherein the pulsation reducing flow path is partitioned in the discharge chamber by the partition wall and the gasket. The discharge chamber communicates with each compression chamber by a discharge port;
The housing has an outlet opening in the discharge chamber adjacent to the communication port, and a discharge passage for guiding the refrigerant in the discharge chamber to the outside of the discharge chamber is formed.
The swash plate compressor according to any one of claims 1 to 3, wherein the communication port and the outlet are disposed downstream of all the discharge ports in the flow direction of the refrigerant in the discharge chamber.

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