JP2008106679A - Reciprocating compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a reciprocating compressor satisfactorily lubricating a sliding contact part of one end surface of a drive shaft with one end surface of a support member. <P>SOLUTION: The reciprocating compressor is provided with a housing having a delivery chamber, a suction chamber, a crank chamber and a plurality of cylinder bores having pistons disposed defined therein, the drive shaft extending in the housing and rotatably supported by the housing, and a conversion mechanism converting rotation of the drive shaft to reciprocating motion of the piston. One end surface of the drive shaft slidably faces to one end surface of the support member disposed in the housing and fixed on the housing. A hole with one end thereof opened on the end surface and with the other end communicating with the crank chamber is formed in the drive shaft. A hole facing the one end of the hole of the drive shaft is formed in the support member. The hole in the drive shaft and the hole in the support member form a part of a communication passage between the crank chamber and the suction chamber. Refrigerant sucked in the cylinder bore from the suction chamber is compressed and delivered to the delivery chamber. The one end of the hole of the drive shaft is formed larger in diameter than the hole in the support member. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a reciprocating compressor.

A housing having a discharge chamber, a suction chamber, a crank chamber, and a plurality of cylinder bores in which pistons are disposed, a drive shaft extending in the housing and rotatably supported by the housing; A conversion mechanism for converting rotation into a reciprocating motion of the piston, and one end surface of the drive shaft is slidably opposed to one end surface of a support member disposed in the housing and fixed to the housing, and one end of the drive shaft A hole that opens in one end surface and communicates with the crank chamber at the other end is formed in the drive shaft, a hole facing the one end of the hole in the drive shaft is formed in the support member, and a hole in the drive shaft and a hole in the support member Patent Document 1 discloses a reciprocating compression that forms a part of a communication path between a crank chamber and a suction chamber, compresses refrigerant sucked into the cylinder bore from the suction chamber, and discharges the refrigerant into the discharge chamber.
Japanese Utility Model Publication 3-41101

In the reciprocating compressor, the communication path between the crank chamber and the suction chamber is formed on the drive shaft, thereby suppressing oil outflow from the crank chamber to the suction chamber.
In the above reciprocating compressor, when the cooling load of the compressor is large, the drive shaft is pressed away from the support member by the gas compression reaction force when the piston compresses the gas, and one end surface of the drive shaft and the support member A small gap is formed between one end surface of the compressor, but when the cooling load of the compressor is small, the discharge capacity of the compressor is reduced, the gas compression reaction force is reduced, and the one end surface of the drive shaft is Make sliding contact with one end surface. Oil outflow from the crank chamber to the suction chamber is suppressed, and the sliding contact portion between one end surface of the drive shaft and one end surface of the support member is in a poorly lubricated state. If it continues, there is a possibility that wear or seizure occurs at the sliding contact portion between the one end surface of the drive shaft and the one end surface of the support member.
The present invention has been made in view of the above problems, and includes a housing in which a discharge chamber, a suction chamber, a crank chamber, and a plurality of cylinder bores provided with pistons are defined, and a housing extending in the housing. And a support member that is disposed in the housing and is fixed to the housing. The drive shaft is rotatably supported by the drive shaft, and a conversion mechanism that converts the rotation of the drive shaft into a reciprocating motion of the piston. A hole is formed in the drive shaft so that one end is slidably contacted with one end surface, the other end is open on the one end surface and the other end communicates with the crank chamber, and a hole facing the one end of the drive shaft hole is the support member. The hole of the drive shaft and the hole of the support member form a part of the communication path between the crank chamber and the suction chamber, compress the refrigerant sucked from the suction chamber into the cylinder bore and discharge it to the discharge chamber The reciprocating compression of the drive shaft Lubrication of the sliding contact portion between the one end face of the end face and the support member and to provide a good reciprocating compressor.

In order to solve the above-described problems, in the present invention, a discharge chamber, a suction chamber, a crank chamber, and a plurality of cylinder bores in which pistons are disposed are defined in the interior, and the housing extends by the housing. A drive shaft rotatably supported; and a conversion mechanism that converts the rotation of the drive shaft into a reciprocating motion of the piston. One end surface of the drive shaft is disposed in the housing and fixed to the housing. A hole is formed in the drive shaft so that one end surface is slidably contacted, one end is opened in the one end surface and the other end communicates with the crank chamber, and a hole facing the one end of the drive shaft hole is formed in the support member. The hole in the drive shaft and the hole in the support member form part of a communication path between the crank chamber and the suction chamber, and compress the refrigerant sucked from the suction chamber into the cylinder bore and discharge it into the discharge chamber. A reciprocating compressor having a drive shaft Wherein one end of the hole to provide a reciprocating compressor, characterized in that has a larger diameter than the pores of the support member.
In the compressor according to the present invention, since the one end of the hole of the drive shaft is formed to have a larger diameter than the hole of the support member, it is centrifuged and directed to the hole of the support member through the peripheral wall of the hole of the drive shaft. The oil flowing in this way is prevented from flowing into the hole of the support member by the step portion between the hole of the drive shaft and the hole of the support member, and accumulates in the step portion. The oil accumulated in the stepped portion is supplied to the sliding contact portion between the one end surface of the drive shaft and the one end surface of the support member by centrifugal force, and lubricates the portion. Therefore, according to the present invention, there is provided a reciprocating compressor in which the oil outflow from the crank chamber to the suction chamber is suppressed and the sliding contact portion between the one end surface of the drive shaft and the one end surface of the support member is well lubricated. .

In a preferred embodiment of the present invention, one end of the hole of the drive shaft forms a funnel-shaped slope that increases in diameter toward the support member.
The oil flowing along the peripheral wall of the hole of the drive shaft is efficiently supplied to the sliding contact portion between the one end surface of the drive shaft and the one end surface of the support member by centrifugal force, so that the lubrication of the portion is further improved.

In a preferred aspect of the present invention, a groove is formed in the one end surface of the drive shaft or the one end surface of the support member so that the hole of the drive shaft communicates with the drive shaft outer peripheral space near the one end surface of the drive shaft. .
In a preferred aspect of the present invention, the reciprocating compressor includes a communication passage that communicates the outer peripheral side space of the drive shaft near the one end surface of the drive shaft with the crank chamber.
Since the oil flowing through the peripheral wall of the hole of the drive shaft is efficiently discharged from the hole and returned to the crank chamber, the oil can be more effectively prevented from flowing out into the suction chamber.

In a preferred aspect of the present invention, the communication path that connects the drive shaft outer peripheral side space near the one end surface of the drive shaft to the crank chamber includes a radial bearing that supports the vicinity of the one end surface of the drive shaft, and the drive shaft outer peripheral surface. It is a gap between.
According to the said structure, since it is not necessary to provide a new oil return channel | path, complication of a compressor structure can be prevented. Further, since the radial bearing can be lubricated with oil that lubricates the sliding contact portion between the one end surface of the drive shaft and the one end surface of the support member, the reliability of the radial bearing is improved.

In a preferred aspect of the present invention, a portion in the vicinity of the hole of the support member surrounding the hole of the support member protrudes into the hole of the drive shaft.
The oil flowing along the peripheral wall of the hole of the drive shaft passes through the annular gap between the vicinity of the hole of the support member protruding into the hole of the drive shaft and the peripheral wall of the hole of the drive shaft, Since it is guided to the sliding contact portion with the one end surface of the support member, the sliding contact portion is well maintained in lubrication, and the reliability of the compressor is improved.

In a preferred aspect of the present invention, a space where the one end face of the support member is in contact with a space where the other end face of the support member facing the one end face is in communication with the lower side of the compressor.
The oil stored in the downstream portion of the communication path between the crank chamber and the suction chamber from the support member can be returned to the crank chamber, so that the oil can be more effectively discharged from the crank chamber to the suction chamber. Can be suppressed.

In a preferred aspect of the present invention, the conversion mechanism has a variable-tilt swash plate or a rocking plate that rotates in synchronization with the drive shaft, and adjusts the pressure in the crank chamber to adjust the maximum inclination angle to the minimum inclination angle. The piston stroke is variably controlled by changing the tilt angle of the swash plate or the swing plate.
Since oil is effectively supplied to the sliding contact portion between the one end surface of the drive shaft and the one end surface of the support member even when the discharge capacity is suppressed in the low load region, good lubrication of the sliding contact portion is maintained and compression is performed. The reliability of the machine is improved.

In a preferred embodiment of the present invention, the hole of the support member forms a throttle disposed in the communication path between the crank chamber and the suction chamber.
Since the throttle is a small hole, the outflow of oil to the suction chamber can be more effectively suppressed.

In a preferred aspect of the present invention, a portion downstream of the throttle in the communication path between the crank chamber and the suction chamber is integrated with the suction chamber.
According to the above configuration, since the suction chamber capacity is increased, the suction pressure pulsation is reduced.

In the compressor according to the present invention, since the one end of the hole of the drive shaft is formed to have a larger diameter than the hole of the support member, it is centrifuged and directed to the hole of the support member through the peripheral wall of the hole of the drive shaft. The oil flowing in this way is prevented from flowing into the hole of the support member by the step portion between the hole of the drive shaft and the hole of the support member, and accumulates in the step portion. The oil accumulated in the stepped portion is supplied to the sliding contact portion between the one end surface of the drive shaft and the one end surface of the support member by centrifugal force, and lubricates the portion. Therefore, according to the present invention, there is provided a reciprocating compressor in which the oil outflow from the crank chamber to the suction chamber is suppressed and the sliding contact portion between the one end surface of the drive shaft and the one end surface of the support member is well lubricated. .

  A reciprocating compressor according to an embodiment of the present invention will be described.

As shown in FIG. 1, the variable capacity swash plate compressor 100 includes a cylinder block 101 in which a plurality of cylinder bores 101 a are defined, a front housing 102 provided at one end of the cylinder block 101, and a valve plate 103. And a rear housing 104 provided at the other end of the cylinder block 101.
A drive shaft 106 is disposed across the crank chamber 105 defined by the cylinder block 101 and the front housing 102. The drive shaft 106 is inserted through the swash plate 107. The swash plate 107 is coupled to a rotor 108 fixed to the drive shaft 106 via a connecting portion 109 and is supported by the drive shaft 106 so that the tilt angle is variable. A coil spring 110 is disposed between the rotor 108 and the swash plate 107 to urge the swash plate 107 toward the minimum inclination angle. On the opposite side of the coil spring 110 across the swash plate 107, a coil spring 111 for urging the swash plate 107 in the minimum tilt state in the direction of increasing the tilt angle is disposed.

One end of the drive shaft 106 passes through the boss portion 102a of the front housing 102 and extends to the outside of the housing, and is directly connected to a vehicle engine (not shown) via a power transmission device (not shown) without using an electromagnetic clutch. . A shaft seal device 112 is disposed between the drive shaft 106 and the boss portion 102a.
The drive shaft 106 is supported in the radial direction and the thrust direction by radial bearings 113 and 114, a thrust bearing 115, and a support member 116.

A piston 117 is disposed in the cylinder bore 101a, and a pair of shoes 118 housed in a recess 117a at one end of the piston 117 sandwich the outer peripheral portion of the swash plate 107 so as to be slidable relative to each other. The rotation of the drive shaft 106 is converted into a reciprocating motion of the piston 117 via the swash plate 107 and the shoe 118.

A suction chamber 119 and a discharge chamber 120 are defined in the rear housing 104. The suction chamber 119 communicates with the cylinder bore 101a via a communication hole 103a formed in the valve plate 103 and a suction valve (not shown), and the discharge chamber 120 communicates with a discharge hole (not shown) and a communication hole 103b formed in the valve plate 103. Is communicated with the cylinder bore 101a. The suction chamber 119 is connected to an evaporator of a vehicle air conditioner (not shown) via a suction port 104a.

A muffler 121 is disposed outside the cylinder block 101. The muffler 121 is formed by joining a bottomed cylindrical lid member 122 separate from the cylinder block 101 to a cylindrical wall 101b erected on the outer surface of the cylinder block 101 via a seal member. . A discharge port 122 a is formed in the lid member 122. The discharge port 122a is connected to a condenser of a vehicle air conditioner (not shown).
A communication passage 123 that allows the muffler 121 to communicate with the discharge chamber 120 is formed across the cylinder block 101, the valve plate 103, and the rear housing 104. The muffler 121 and the communication passage 123 form a discharge passage extending between the discharge chamber 120 and the discharge port 122a, and the muffler 121 forms an expansion space arranged in the middle of the discharge passage. Yes.
A check valve 200 that opens and closes the inlet of the muffler 121 is disposed in the muffler 121. The check valve 200 closes the inlet of the muffler 121 when the variable capacity swash plate compressor 100 is operated at the minimum discharge capacity, interrupts the refrigerant circulation to the vehicle air conditioner, and performs unnecessary air conditioning. To prevent.

The front housing 102, the cylinder block 101, the valve plate 103, and the rear housing 104 are adjacent to each other through a gasket (not shown), and are integrally assembled using a plurality of through bolts.

A capacity control valve 300 is attached to the rear housing 104. The capacity control valve 300 senses the suction chamber pressure by the communication passage 124 and adjusts the energization amount to the built-in solenoid, adjusts the opening degree of the communication passage 125 between the discharge chamber 120 and the crank chamber 105, The amount of discharge refrigerant gas introduced into the chamber 105 is controlled to control the tilt angle of the swash plate, and the discharge capacity is controlled so as to achieve a predetermined suction chamber pressure. Further, by stopping energization to the solenoid and forcibly opening the communication path 125, the discharge capacity is controlled to the minimum.

The refrigerant gas in the crank chamber 105 is formed in the cylinder block 101, the center hole 101c formed in the cylinder block 101, the hole 106a formed in the drive shaft 106, the hole 116a formed in the support member 116, and the cylinder block 101. It flows into the suction chamber 119 through a communication path between the crank chamber 105 and the suction chamber 119 formed by the space 126 and the orifice hole 103 c formed in the valve plate 103.

As shown in FIG. 2, the one end surface 106 b of the drive shaft 106 faces the one end surface 116 b of the support member 116 press-fitted and fixed to the cylinder block 101 so as to be slidable.
One end 106 a ′ of the hole 106 a formed in the drive shaft 106 opens to the one end surface 106 b of the drive shaft 106 and faces the hole 116 a of the support member 116. One end 106a 'of the drive shaft hole 106a is formed to have a larger diameter than the hole 116a of the support member. A funnel-shaped slope 106c is formed at one end 106a 'of the hole 106a, and expands toward the one end surface 116b of the support member.
The other end 106a ″ of the drive shaft hole 106a opens on the peripheral side surface of the drive shaft 106, and communicates with the crank chamber 105 through the center hole 101c of the cylinder block.
The hole 116a of the support member faces the one end 106a ′ of the hole of the drive shaft and communicates with a space 126 formed in the cylinder block. One end surface 116 b of the support member 116 is in contact with a drive shaft outer circumferential side space 127 described later, and the other end surface facing the one end surface 116 b is in contact with the space 126.

The drive shaft outer peripheral space 127 in the vicinity of the one end surface 106b of the drive shaft 106 passes through a gap between the radial bearing 114 that supports the vicinity of the one end surface 106b of the drive shaft 106 in the radial direction and the outer peripheral surface of the drive shaft 106. The cylinder block communicates with the center hole 101c of the cylinder block, and thus communicates with the crank chamber 105. An inclined groove 101d that is inclined downward toward the crank chamber 105 is formed below the center hole 101c of the cylinder block.

The operation of the variable capacity swash plate compressor 100 will be described.
When the vehicle air conditioner is operated, a current flows through the solenoid of the capacity control valve 300 and the communication path 125 is blocked. Since the gas in the crank chamber 105 flows out to the suction chamber 119 via the communication path between the crank chamber 105 and the suction chamber 119, the internal pressure of the crank chamber 105 is reduced and becomes equal to the internal pressure of the suction chamber 119. The inclination angle of the swash plate 107 increases, and the stroke of the piston 117 increases. When the internal pressure of the discharge chamber 120 increases and the differential pressure across the check valve 200 exceeds a predetermined value, the check valve 200 is opened and the inlet of the muffler 121 is opened. The discharge chamber 120 communicates with the muffler 121 through the communication passage 123 and the check valve 200, and the refrigerant gas circulates to the vehicle air conditioner through the discharge port 122a.
The energization amount to the solenoid of the capacity control valve 300 is appropriately controlled based on the external signal, the opening degree of the communication path 125 is appropriately controlled, and the discharge capacity of the variable capacity swash plate compressor 100 is appropriately controlled. .

When the internal pressure of the discharge chamber 120 increases, the drive shaft 106 is pressed away from the support member 116 by the gas compression reaction force when the piston 117 compresses the gas in the cylinder bore 101a, as shown in FIG. In addition, a minute gap X is formed between one end surface 106 b of the drive shaft 106 and one end surface 116 b of the support member 116. Accordingly, a thrust load does not act on the support member 116.
The blow-by gas when the piston 117 compresses the gas flows into the crank chamber 105, and the gas in the discharge chamber 120 also flows in via the capacity control valve 300 during the capacity control operation. The gas flows along with the oil into the hole 106a of the drive shaft through the center hole 101c. The gas flowing into the hole 106a from the other end 106a ″ of the hole 106a collides with the peripheral wall of the hole 106a, receives the centrifugal force due to the rotation of the drive shaft, separates the oil from the gas, and adheres to the peripheral wall of the hole 106a. It flows into the hole 116a of the support member from one end 106a 'of the hole 106a, and further flows into the suction chamber 119 through the space 126 and the orifice hole 103c.

The oil separated from the gas flows downstream along the peripheral wall of the hole 106a, receives the centrifugal force, and receives the centrifugal force from the minute gap X between the one end surface 106b of the drive shaft 106 and the one end surface 116b of the support member 116. It scatters to the outer peripheral space 127 and is stored in the lower part of the space 127. When the liquid level of the stored oil exceeds the height of the lower edge of the gap between the radial bearing 114 and the outer periphery of the drive shaft 106, the oil becomes a gap between the radial bearing 114 and the outer peripheral surface of the drive shaft 106. After the radial bearing 114 is lubricated via the lower portion of the lower portion, the shaft returns to the center hole 101c and returns to the crank chamber 105 through the inclined groove 101d of the center hole.

When the vehicle air conditioner is inactive when the vehicle engine is in operation, no current flows through the solenoid of the displacement control valve 300, the communication path 125 is forcibly opened, and the gas in the discharge chamber 120 enters the crank chamber 105 via the communication 125. As a result, the internal pressure of the crank chamber 105 increases, the inclination angle of the swash plate 107 decreases, and the discharge capacity of the variable displacement swash plate compressor 100 is minimized. The check valve 200 closes the inlet of the muffler 121. Therefore, the variable capacity swash plate compressor 100 directly connected to the vehicle engine is operated with the minimum discharge capacity, but the refrigerant circulation to the vehicle air conditioner is blocked. As a result, the occurrence of unnecessary air conditioning is prevented.
The refrigerant gas discharged from the cylinder bore 101a to the discharge chamber 120 with the minimum discharge capacity is a communication path 125 between the discharge chamber 120 including the capacity control valve 300 and the crank chamber 105, the crank chamber 105, the center hole 101c, It circulates in the internal circulation circuit that returns to the cylinder bore 101a through the drive shaft hole 106a, the support member hole 116a, the space 126, the orifice hole 103c, the suction chamber 119, and the communication hole 103a.

Since the communication passage 125 is forcibly opened and the gas in the discharge chamber 120 flows into the crank chamber 105, the internal pressure of the crank chamber 105 increases, the piston back pressure increases, and the drive shaft 106 moves toward the valve plate 103. To do. As a result, the one end surface 106 b of the drive shaft 106 is in sliding contact with the one end surface 116 b of the support member 116.
If a communication path between the crank chamber 105 and the suction chamber 119 is formed in the drive shaft 106 in order to suppress oil outflow from the crank chamber 105 to the suction chamber 119, one end surface 106b of the drive shaft and one end surface 116b of the support member are formed. The sliding contact portion tends to be poorly lubricated. However, in the variable capacity swash plate compressor 100, since one end 106a 'of the drive shaft hole 106a is formed to have a larger diameter than the hole 116a of the support member 116, the support member is transmitted along the peripheral wall of the drive shaft hole 106a. The oil flowing toward the hole 116a is prevented from flowing into the hole 116a of the support member by the step between the one end 106a ′ of the hole 106a of the drive shaft and the hole 116a of the support member. Accumulate. The oil accumulated in the stepped portion is pushed into the sliding contact portion between the one end surface 106b of the drive shaft and the one end surface 116b of the support member by centrifugal force, and lubricates the portion. Therefore, in the variable capacity swash plate compressor 100, the outflow of oil from the crank chamber 105 to the suction chamber 119 is suppressed, and the sliding contact portion between the one end surface 106b of the drive shaft and the one end surface 116b of the support member is excellent. Lubricated.

The oil accumulated in the step between the one end 106a 'of the drive shaft hole 106a and the support member hole 116a is directed to one end surface 116b of the support member 116 formed at one end 106a' of the drive shaft hole 106a. Then, it is guided by the funnel-shaped slope 106c that expands in diameter and efficiently supplied to the sliding contact portion between the one end surface 106b of the drive shaft and the one end surface 116b of the support member. As a result, the lubrication of the sliding contact portion between the one end face 106b of the drive shaft and the one end face 116b of the support member is further improved.

The oil that has lubricated the sliding contact portion between the one end face 106 b of the drive shaft and the one end face 116 b of the support member flows into the drive shaft outer peripheral space 127 and is stored in the lower portion of the space 127. When the liquid level of the stored oil exceeds the height of the race of the radial bearing 114, the oil passes through the lower portion of the gap between the radial bearing 114 and the outer peripheral surface of the drive shaft 106 and passes through the radial bearing 114. After lubrication, it returns to the center hole 101c, returns to the crank chamber 105 through the inclined groove 101d of the center hole.
The oil discharged from the drive shaft hole 106a and flowing into the space 127 returns to the crank chamber 105 through the communication path between the space 127 and the crank chamber 105, so that the oil can be more effectively discharged into the suction chamber 119. Can be suppressed.
Since the gap between the radial bearing 114 and the outer peripheral surface of the drive shaft 106 forms a communication path between the drive shaft outer peripheral space 127 and the crank chamber 105, there is no need to provide a new oil return passage, and compression is performed. The complexity of the machine structure can be prevented. Further, since the radial bearing 114 can be lubricated with oil that lubricates the sliding contact portion between the one end face 106b of the drive shaft and the one end face 116b of the support member, the reliability of the radial bearing 114 is improved.

In order to enhance the effect of pushing the oil into the sliding contact portion between the one end surface 106b of the drive shaft and the one end surface 116b of the support member by centrifugal force, the diameter of the hole 106a of the drive shaft is as large as possible within the range allowed by design. It is desirable to do.

As shown in FIG. 3, a groove 116 c that allows the drive shaft hole 106 a to communicate with the drive shaft outer peripheral space 127 may be formed in the one end surface 116 b of the support member. As indicated by a one-dot chain line in FIG. 3, a groove 106d that connects the drive shaft hole 106a to the drive shaft outer circumferential space 127 may be formed on one end face 106b of the drive shaft.
Since the oil flowing along the peripheral wall of the drive shaft hole 106a is efficiently discharged from the hole and returned to the crank chamber 105, the oil outflow into the suction chamber 105 can be further effectively suppressed.

As shown in FIG. 4, a hole vicinity portion 116d of the support member 116 surrounding the hole 116a of the support member 116 may protrude into the hole 106a of the drive shaft.
Oil flowing along the peripheral wall of the drive shaft hole 106a passes through an annular gap 106e between the hole vicinity portion 116d of the support member 116 protruding into the drive shaft hole 106a and the peripheral wall of the drive shaft hole 106a. Since it is guided to the sliding contact portion between the one end surface 106b of the drive shaft and the one end surface 116b of the support member, the sliding contact portion is well maintained and the reliability of the compressor is improved.

As shown in FIG. 5, the support member that slidably contacts the one end surface 106 b of the drive shaft 106 is engaged with the hole 116 a that faces the hole 106 a of the drive shaft and the upper and lower grooves 101 e formed in the cylinder block 101. The support member 116 having the rotation stopper 116e to be joined, and the support member 116 is positioned so that a predetermined minute gap X is formed between the one end surface 106b of the drive shaft 106 and the one end surface 116b of the support member 116. You may comprise with the adjustment member 128 fixed to the cylinder block 101. FIG. The adjustment member 128 is formed with a hole 128a communicating with the hole 116a of the support member. The adjusting member 128 is screwed into the cylinder block 101, positioned, and then fixed to the cylinder block 101 by caulking. A groove 106 d that allows the drive shaft hole 106 a to communicate with the drive shaft outer peripheral space 127 may be formed on one end surface of the drive shaft 106.
Further, the radial bearing 114 is a sliding bearing 114 ′, and oil accumulated in the lower portion of the drive shaft outer peripheral space 127 is returned to the center hole 101 c via the communication passage 129 formed in the cylinder block 101, and the crank chamber 105 is returned from the center hole 101 c. You may return to.
The space 126 and the space 127 communicate with each other via upper and lower grooves 101e formed in the cylinder block 101, and the oil stored in the space 126 is also transferred to the lower groove 101e, the space 127, the communication path 129, the center hole. It is returned to the crank chamber 105 via 101c. As a result, the oil outflow from the crank chamber 105 to the suction chamber 119 is further effectively suppressed.

As shown in FIG. 6, the hole 116 a of the support member 116 may form a throttle disposed in the communication path between the crank chamber 105 and the suction chamber 119.
Since the throttle is a small hole, the outflow of oil to the suction chamber 119 can be more effectively suppressed. Further, according to the above configuration, the orifice hole 103 c formed in the valve plate can be expanded to the same diameter as the space 126, the space 126 can be integrated with the suction chamber 119, and the capacity of the suction chamber 119 can be increased. As the capacity of the suction chamber 119 increases, the suction pressure pulsation decreases.

The diameter of the drive shaft hole 106a may be gradually increased toward the one end 106a ′.
The funnel-shaped slope 106c formed at one end 106a 'of the drive shaft hole 106a may be curved.
A plurality of grooves 116 c may be formed on one end surface 116 b of the support member 116, or a plurality of grooves 106 d may be formed on one end surface 106 b of the drive shaft 106.
Since the other end 106 a ″ of the hole 106 a of the drive shaft only needs to communicate with the crank chamber 105, it may be disposed at an arbitrary position between the shaft seal device 112 and the radial bearing 114.
The present invention is applicable to various reciprocating compressors other than the variable displacement swash plate compressor, such as a variable displacement oscillating plate compressor, a fixed displacement swash plate compressor, and a fixed displacement oscillating plate compressor.
The present invention is applicable to various reciprocating compressors connected to an external drive source via an electromagnetic clutch.
The present invention is applicable to various reciprocating compressors using a motor as an external drive source.
Instead of the current R134a, CO2 or R152a may be used as the refrigerant.

The present invention is widely applicable to various reciprocating compressors.

It is sectional drawing of the variable capacity | capacitance swash plate type compressor which concerns on 1st Example of this invention. It is the elements on larger scale of FIG. (A), (c) shows a state where one end surface of the drive shaft is in sliding contact with one end surface of the support member, and (b) shows a minute gap formed between one end surface of the drive shaft and one end surface of the support member. Indicates the state that has been performed. It is a partial expanded sectional view of the variable capacity | capacitance swash plate type compressor which concerns on 2nd Example of this invention. It is a partial expanded sectional view of the variable capacity | capacitance swash plate type compressor which concerns on 3rd Example of this invention. It is a partial expanded sectional view of the variable capacity | capacitance swash plate type compressor which concerns on 4th Example of this invention. (A) is sectional drawing, (b) is a bb arrow line view of (a). It is a partial expanded sectional view of the variable capacity | capacitance swash plate type compressor which concerns on 5th Example of this invention.

Explanation of symbols

100 Variable capacity swash plate compressor 105 Crank chamber 106 Drive shaft 106a Hole 107 Swash plate 116 Support member 116a Hole 117 Piston 119 Suction chamber 120 Discharge chamber 200 Check valve 300 Capacity control valve

Claims (10)

A housing having a discharge chamber, a suction chamber, a crank chamber, and a plurality of cylinder bores in which pistons are disposed, a drive shaft extending in the housing and rotatably supported by the housing; A conversion mechanism for converting rotation into a reciprocating motion of the piston, and one end surface of the drive shaft is slidably opposed to one end surface of a support member disposed in the housing and fixed to the housing, and one end of the drive shaft A hole that opens in one end surface and communicates with the crank chamber at the other end is formed in the drive shaft, a hole facing the one end of the hole in the drive shaft is formed in the support member, and a hole in the drive shaft and a hole in the support member Is a reciprocating compressor that forms a part of the communication path between the crank chamber and the suction chamber, compresses the refrigerant sucked from the suction chamber into the cylinder bore, and discharges it to the discharge chamber. The one end is formed larger in diameter than the hole of the support member Reciprocating compressor, characterized by being. The reciprocating compressor according to claim 1, wherein one end of the hole of the drive shaft forms a funnel-shaped inclined surface whose diameter increases toward the support member. 2. A groove is formed in the one end surface of the drive shaft or the one end surface of the support member to communicate a hole of the drive shaft with a drive shaft outer peripheral side space in the vicinity of the one end surface of the drive shaft. Or the reciprocating compressor as described in 2. The reciprocating compressor according to claim 3, further comprising a communication passage that communicates a drive shaft outer peripheral side space in the vicinity of the one end surface of the drive shaft with the crank chamber. The communication path that connects the drive shaft outer peripheral side space in the vicinity of the one end surface of the drive shaft to the crank chamber is a gap between a radial bearing that supports the vicinity of the one end surface of the drive shaft and the outer peripheral surface of the drive shaft. The reciprocating compressor according to claim 4. The reciprocating compressor according to any one of claims 1 to 5, wherein a portion in the vicinity of the hole of the support member surrounding the hole of the support member protrudes into the hole of the drive shaft. The space where the one end surface of the support member is in contact with the space where the other end surface of the support member facing the one end surface is in communication on the lower side of the compressor. A reciprocating compressor according to claim 1. The conversion mechanism has a swash plate or oscillating plate with a variable tilt angle that rotates in synchronization with the drive shaft. By adjusting the pressure in the crank chamber, the swash plate or oscillating plate can be moved between the maximum tilt angle and the minimum tilt angle. The reciprocating compressor according to any one of claims 1 to 7, wherein the piston stroke is variably controlled by changing an inclination angle. The reciprocating compressor according to claim 8, wherein the hole of the support member forms a throttle disposed in a communication path between the crank chamber and the suction chamber. The reciprocating compressor according to claim 9, wherein a portion of the communication path between the crank chamber and the suction chamber downstream of the throttle is integrated with the suction chamber.

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