JP2013117185A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor which can suppress a rise of a temperature of an abutting portion between an abutting member and an abutted member.SOLUTION: A compressor 100 comprises: a cylinder block 110; a front housing 120; a cylinder head 130; a valve plate 140; a suction valve forming plate 171; a discharge valve forming plate 175; a drive shaft 150; an abutting member 160 fixed at the end of the drive shaft at the side of the cylinder head; the abutted member 170 arranged between the cylinder block and the cylinder head; a piston 112; and a conversion mechanism 122 for converting the rotation of the drive shaft to reciprocating motion. An abutting face of the abutting member 160 which abuts on the abutted member 170 is formed into an annular shape, and a region 172 in which the pressure of a refrigerant received in a suction chamber 133 acts is set at least at a portion of a face at a side opposite to the drive shaft side of the region inside an abutment 173 on which the abutting face abuts out of surfaces of the abutted member 170.

Description

  The present invention relates to a swash plate compressor, and more specifically, by setting a region where the pressure of a refrigerant accommodated in a suction chamber acts on at least a part of a surface of a member to be abutted against which the abutting member abuts. The present invention relates to a compressor capable of suppressing a temperature rise at a contact portion between a contact member and a contacted member.

  As a conventional compressor, a compression chamber in which refrigerant gas is compressed, a suction chamber into which refrigerant gas sucked into the compression chamber is introduced, and a discharge chamber into which refrigerant gas discharged from the compression chamber is introduced A variable capacity mechanism capable of changing the discharge capacity, a control chamber in which an internal pressure is adjusted to control the variable capacity mechanism, an air supply passage communicating the discharge chamber and the control chamber, the control chamber and the suction chamber There has been a variable displacement compressor provided with a bleed passage that communicates with a chamber and a drive shaft that is rotationally driven by an external drive source in order to obtain power for compressing refrigerant gas in the compression chamber (for example, Patent Document 1).

  Such a compressor is disposed on the bleed passage and is connected to a drive shaft, and rotates with the rotation of the drive shaft, thereby centrifuging oil from refrigerant gas flowing in the bleed passage. (Abutment member), an oil chamber provided in the housing, into which oil that has been centrifuged by the abutment member is introduced and an internal pressure is maintained at or above the internal pressure of the control chamber, provided in the housing, And an oil return passage for returning the oil in the oil chamber to the control chamber.

  The drive shaft is regulated so that the sliding movement in the direction close to the valve / port formation body is restricted by the flange portion of the contact member coming into contact with the suction valve formation plate of the valve / port formation body. It was. Therefore, the front side of the intake valve forming plate of the valve / port forming body functions as a rear side movement restricting portion (contacted member) for restricting sliding movement of the drive shaft to the rear side of the axis.

  Further, as a conventional compressor, a housing including a suction chamber and a discharge chamber, a crank chamber defined in the housing, and a first end portion that is rotatably supported by the housing so as to protrude from the housing. A drive shaft, a cylinder bore formed in a cylinder block that forms a part of the housing, and a suction port, a suction valve, a discharge port, and a discharge port that are installed in the housing to close the cylinder bore. A valve / port forming body having a valve, a single-headed piston accommodated in the cylinder bore so as to be reciprocally movable, and accommodated in the crank chamber, for converting the rotational motion of the drive shaft into the reciprocating motion of the piston. A cam plate operatively connected to the piston, and controlling the pressure in the crank chamber to control the cam plate. There is a variable capacity compressor provided with a tilt control means for controlling the inclination angle of over bets from the cylinder bore due to the reciprocation of the piston to vary the discharge capacity to the discharge chamber (e.g. see Patent Document 2).

  In such a compressor, one end of the compressor is connected to a housing hole in which a radial bearing that supports the second end (contact member) of the drive shaft is provided in the housing, and the other end is the valve / port forming body. A housing member that is closed by the passage, the housing chamber and the suction chamber communicate with each other through a passage, and a regulating member that restricts the drive shaft from moving to the second end side in the housing chamber A contact member) divides the storage chamber into an opening side region of the passage and a radial bearing side region, and during the normal compression operation, the drive shaft and the restriction member or the restriction member and the valve / port There is a slight gap between the formed body and the clearance when the pressure in the crank chamber is suddenly increased, so that the gap becomes zero and restricts the movement of the drive shaft, and is partitioned by the restriction member. Said opening It had formed a path for communicating the region and the radial bearing side region.

JP 2002-213350 A JP 2002-13474 A

  However, in the conventional compressor, when the contact member contacts the contacted member while rotating as the drive shaft rotates, the contact between the contact member and the contacted member There was a possibility that sliding heat generation might increase at the portion. For this reason, when the lubrication at the contact portion is insufficient, there is a possibility that seizure occurs at the contact portion.

  Accordingly, a problem to be solved by the present invention that addresses such problems is to provide a compressor that can suppress an increase in the temperature of the contact portion between the contact member and the contacted member. is there.

In order to solve the above problems, a compressor according to the present invention includes a cylinder block in which a plurality of cylinder bores are defined, a front housing attached to one end of the cylinder block and having a crank chamber formed therein, and the cylinder block. A cylinder head in which a suction chamber for storing refrigerant sucked from the refrigerant circuit and a discharge chamber for storing refrigerant discharged to the refrigerant circuit are formed; and the cylinder block and the cylinder A valve plate provided between the head and formed with a suction hole for communicating the cylinder bore and the suction chamber; and a discharge hole for communicating the cylinder bore and the discharge chamber; the cylinder block and the valve A refrigerant flow from the suction chamber to the cylinder bore through the suction hole. An intake valve forming plate having an intake valve that allows the discharge of refrigerant, and is provided between the valve plate and the cylinder head, and allows the refrigerant to be discharged from the cylinder bore into the discharge chamber via the discharge hole. A discharge valve forming plate having a discharge valve formed thereon, a drive shaft rotatably supported by the cylinder block and the front housing, a contact member fixed to an end of the drive shaft on the cylinder head side, and A contact member provided between a cylinder block and the cylinder head, which contacts the contact member and restricts movement of the drive shaft toward the cylinder head; and a piston disposed in the plurality of cylinder bores And a conversion mechanism that converts the rotation of the drive shaft into the reciprocating motion of the piston.
The contact surface of the contact member that contacts the contacted member is formed in an annular shape, and drives the region inside the contact portion that contacts the contact surface, of the surface of the contacted member. A region where the pressure of the refrigerant accommodated in the suction chamber acts is set on at least a part of the surface opposite to the shaft side.

  According to the compressor of the present invention, the suction member is disposed on at least a part of the surface of the contacted member on the side opposite to the drive shaft side in the region inside the contact portion with which the contact member contacts. The pressure of the refrigerant accommodated in the chamber can be applied. Therefore, even when the contact member fixed to the drive shaft contacts the contacted member while rotating with the rotation of the drive shaft, the contact between the contact member and the contacted member is not achieved. The contact portion is cooled by the refrigerant accommodated in the suction chamber, and an increase in temperature of the contact portion can be suppressed. Thereby, even when the lubrication at the contact portion is insufficient, the occurrence of seizure at the contact portion can be suppressed.

It is sectional drawing which shows 1st Embodiment of the compressor by this invention. It is a principal part expanded sectional view of the compressor shown in FIG. It is a principal part expanded sectional view which shows 2nd Embodiment of the compressor by this invention. It is a principal part expanded sectional view which shows 3rd Embodiment of the compressor by this invention. It is sectional drawing which shows 4th Embodiment of the compressor by this invention. It is a principal part expanded sectional view of the compressor shown in FIG.

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
FIG. 1 is a cross-sectional view showing a first embodiment of a compressor 100 according to the present invention. The compressor 100 is a variable capacity compressor that controls a refrigerant discharge capacity by changing an inclination angle of a swash plate 122c formed in a front housing 120 described later. In the present embodiment, the compressor 100 is a clutchless compressor that does not use a clutch, and is used, for example, in a vehicle air conditioner (car air conditioner).

  The compressor 100 includes a cylinder block 110, a front housing 120, a cylinder head 130, a valve plate 140, a drive shaft 150, a contact member 160, and a contacted member 170.

  The cylinder block 110 forms a housing of the compressor 100 together with the front housing 120 and the cylinder head 130. The cylinder block 110 includes a cylinder bore 111, a piston 112, a radial bearing 113, a first suction communication hole 114, and a first discharge communication hole 115.

  The cylinder bore 111 is a space for compressing the refrigerant sucked from the refrigerant pipe. A plurality of cylinder bores 111 are concentrically defined in the cylinder block 110.

  A piston 112 is disposed in the cylinder bore 111. The piston 112 reciprocates in the cylinder bore 111, thereby changing the volume of the refrigerant accommodated in the cylinder bore 111 and compressing the refrigerant. An end 112a of the piston 112 on the front housing 120 side (left side in FIG. 1) protrudes from the cylinder block 110 to the front housing 120 side, and is accommodated in a crank chamber 121 formed in the front housing 120 described later. .

  The end 112a accommodates the outer periphery of the swash plate 122c via a pair of opposed shoes 112b. Accordingly, the piston 112 can reciprocate in the cylinder bore 111 in conjunction with the rotation of the swash plate 122c.

  A radial bearing 113 is provided at the center of the cylinder block 110. The radial bearing 113 is for rotatably supporting the drive shaft 150, and is formed so as to surround the outer periphery of the drive shaft 150. The drive shaft 150 is supported in the radial direction (radial direction) by the radial bearing 113.

  A first suction communication hole 114 is formed at the center of the cylinder block 110. The first suction communication hole 114 is a refrigerant flow path that connects the crank chamber 121 of the front housing 120 and a suction chamber 133 formed in a cylinder head 130 described later, and includes a first space 114a and a second space 114b. And a communication hole 114c.

  The first space 114 a is open to the crank chamber 121 side, and is formed closer to the front housing 120 than the radial bearing 113. A tilt-increasing spring 153 mounted on a drive shaft 150 described later is accommodated in the first space 114a.

  On the other hand, the second space 114b is open to the suction chamber 133 side, and is formed closer to the cylinder head 130 than the radial bearing 113. A contact member 160 is accommodated in the second space 114b.

  A communication hole 114c is formed between the first space 114a and the second space 114b to connect the spaces 114a and 114b. The communication hole 114 c is formed outside the radial bearing 113. A plurality of communication holes 114c may be formed.

  Further, a first discharge communication hole 115 is formed in the cylinder block 110. The first discharge communication hole 115 is a refrigerant flow path that allows communication between a crank chamber 121 of the front housing 120 and a discharge chamber 134 of a cylinder head 130 described later. The refrigerant in the discharge chamber 134 flows into the crank chamber 121 through the first discharge communication hole 115. The first discharge communication hole 115 is connected to a control valve 136 provided in a cylinder head 130 described later.

  A muffler 116 is provided on the upper part of the cylinder block 110 (upper part in FIG. 1). The muffler 116 includes a lid member 116a, a wall 116b, a communication passage 116c, a check valve 116d, a muffler space 116e, and a discharge port 116f.

  The outer wall of the muffler 116 is formed by fastening a lid member 116a and a wall portion 116b formed on the upper portion of the cylinder block 110 with bolts. The lid member 116a and the wall portion 116b are fastened via a seal member (not shown) for preventing the refrigerant from leaking.

  Inside the muffler 116, a communication path 116c opened to the cylinder head 130 side is formed. The communication path 116 communicates with a discharge chamber 134 of a cylinder head 130 described later.

  A check valve 116d is provided at the end of the communication passage 116c opposite to the discharge chamber 134. The check valve 116d operates in accordance with a pressure difference between the communication path 116c and the muffler space 116e. When the pressure difference is smaller than a predetermined value, the check path 116d is shut off, and the pressure difference is greater than or equal to a predetermined value. Opens the communication path 116c.

  A discharge port 116f communicates with the muffler space 116e. The discharge port 116f is a connection portion that connects the compressor 100 and an external refrigerant circuit, and is connected to the refrigerant circuit on the discharge side. The high-temperature refrigerant compressed by the compressor 100 is discharged from the discharge port 116f to the refrigerant circuit.

  Therefore, the refrigerant stored in the discharge chamber 134 passes through the communication path 116c, the check valve 116d, and the muffler space 116e, and is discharged from the discharge port 116f to the refrigerant circuit.

  A front housing 120 is attached to one end side of the cylinder block 110. The front housing 120 is connected to the cylinder block 110 to form the housing of the compressor 100. The front housing 120 includes a crank chamber 121, a boss portion 124, a shaft seal device 126, and a communication passage 127, and a conversion mechanism 122, a thrust bearing 123, and a radial bearing 125 are accommodated therein. Has been.

  The crank chamber 121 is a space formed inside the front housing 120, which is defined by the front housing 120 and one end of the cylinder block 110. A drive shaft 150 that is rotatably supported by the front housing 120 is provided across the center of the crank chamber 121. A conversion mechanism 122 that converts the rotation of the drive shaft 150 into the reciprocating motion of the piston 112 is provided in the crank chamber 121.

  The conversion mechanism 122 includes a rotor 122a, a link mechanism 122b, and a swash plate 122c. The rotor 122 a is a disk-like member that is fixed to the drive shaft 150 and rotates together with the drive shaft 150. The rotor 122a is disposed in the vicinity of the wall surface of the crank chamber 121 opposite to the cylinder block 110.

  A link mechanism 122b is connected to the rotor 122a. The link mechanism 122b connects the rotor 122a and the swash plate 122c so that the inclination angle of the swash plate 122c is variable. The link mechanism 122b includes a first arm 122p that protrudes from the rotor 122a, a second arm 122q that protrudes from the swash plate 122c, and a link arm 122r that connects the first arm 122p and the second arm 122q. Prepare.

  One end of the link arm 122r is rotatably connected to the first arm 122p via the first connecting pin 122s, and the other end of the link arm 122r is rotatable to the second arm 122q via the second connecting pin 122t. It is connected.

  The swash plate 122c is a disk-like member having a through hole 122h through which the drive shaft 150 passes at the center. Since the swash plate 122c is connected to the rotor 122a fixed to the drive shaft 150 via the link mechanism 122b, the swash plate 122c rotates together with the drive shaft 150. As the swash plate 122c rotates with respect to a plane perpendicular to the drive shaft 150, the piston 112 reciprocates via the shoe 112b.

  The inclination angle θ of the swash plate 122c with respect to the plane perpendicular to the drive shaft 150 is variable between the maximum inclination angle θmax and the minimum inclination angle θmin. The through-hole 122h is shaped so that the swash plate 122c can tilt within the range from the maximum tilt angle θmax to the minimum tilt angle θmin, and the tilt angle θ of the swash plate 122c is the maximum tilt angle θmax. There is a maximum tilt angle restricting portion 122i that comes into contact with the drive shaft 150 in some cases, and a minimum tilt angle restricting portion 122j that comes into contact with the drive shaft 150 when the tilt angle θ is the minimum tilt angle θmin.

  Here, the inclination angle θ of the swash plate 122c is 0 degree when the swash plate 122c is in a state parallel to the plane perpendicular to the drive shaft 150, that is, the swash plate 122c is perpendicular to the drive shaft 150. To increase. Therefore, θmin = 0 degrees.

  A thrust bearing 123 is provided between the rotor 122 a of the conversion mechanism 122 and the wall surface of the crank chamber 121 opposite to the cylinder block 110. The thrust bearing 123 is in contact with the rotor 122a and supports the drive shaft 150 in the thrust direction (axial direction). Through this thrust bearing 123, a part of the rotor 122a and the wall surface of the crank chamber 121 opposite to the cylinder block 110 come into contact with each other, so that the drive shaft 150 is opposite to the cylinder head 130 (the left side in FIG. 1). ) Is restricted.

  The front housing 120 is formed with a boss portion 124 that protrudes on the opposite side of the cylinder block 110. A radial bearing 125 is provided at the center of the boss portion 124. The radial bearing 125 is for rotatably supporting the drive shaft 150 and is formed so as to surround the outer periphery of the drive shaft 150. The drive shaft 150 is supported by a radial bearing 125 in the radial direction (radial direction).

  A shaft seal device 126 is inserted into the boss portion 124. The shaft seal device 126 blocks the inside and the outside of the front housing 120. The shaft seal device 126 can prevent the refrigerant in the crank chamber 121 from leaking to the outside.

  Further, the boss portion 124 is formed with a communication passage 127 that communicates the crank chamber 121 and the space in which the shaft seal device 126 is disposed. Oil in the refrigerant scattered on the inner wall of the crank chamber 121 flows into the space where the shaft seal device 126 is disposed through the communication path 127. Thereby, the radial bearing 125 and the shaft seal device 126 can be lubricated.

  A cylinder head 130 is attached to the other end side of the cylinder block 110, that is, the opposite side of the front housing 120. The cylinder head 130 is connected to the cylinder block 110 to form a housing of the compressor 100. The cylinder head 130 includes a suction port 131, a communication path 132, a suction chamber 133, a discharge chamber 134, a second discharge communication hole 135, and a control valve 136.

  The suction port 131 is a connection part that connects the compressor 100 and an external refrigerant circuit, and is connected to the refrigerant circuit on the suction side. Low-temperature refrigerant that has circulated through the refrigerant circuit is drawn into the compressor 100 from the suction port 131.

  A communication path 132 is formed so as to communicate with the suction port 131. The communication path 132 extends linearly in the radial direction of the cylinder head 130 so as to cross a part of a discharge chamber 142 described later.

  An end portion of the communication path 132 opposite to the suction port 131 communicates with the suction chamber 133. The suction chamber 133 is formed at the center of the cylinder head 130 and opens toward the cylinder block 120 so as to cover a flange portion 163 of a contact member 160 described later. The refrigerant sucked from the suction port 131 is accommodated in the suction chamber 133 through the communication path 132.

  A discharge chamber 134 is formed outside the suction chamber 133 of the cylinder head 130 so as to surround the suction chamber 133. The discharge chamber 134 opens to the cylinder block 120 side so as to communicate with the cylinder bore 111. The refrigerant discharged to the refrigerant circuit compressed by the cylinder bore 111 is accommodated in the discharge chamber 134.

  A second discharge communication hole 135 is formed in the discharge chamber 134 so as to communicate therewith. The second discharge communication hole 135 opens to the cylinder block 110 side and communicates with the first discharge communication hole 115.

  Further, the cylinder head 130 is provided with a control valve 136. The control valve 136 adjusts the opening degree of the discharge communication path 104 described later, and controls the amount of refrigerant stored in the discharge chamber 134 into the crank chamber 121. The control valve 136 has a built-in solenoid (not shown), and the amount of refrigerant flowing into the crank chamber 121 can be controlled by controlling the amount of current supplied to the solenoid based on an external signal. Since the refrigerant contains oil, lubrication of each part in the crank chamber 121 can be promoted by opening the control valve 136 and allowing the refrigerant to flow into the crank chamber 121.

  A valve plate 140 is provided between the cylinder block 110 and the cylinder head 130. The valve plate 140 includes a suction hole 141, a discharge hole 142, a communication hole 143, a crank hole 144, and a third discharge communication hole 145.

  The suction hole 141 is an opening through which the suction chamber 133 of the cylinder head 130 communicates with the cylinder bore 111 of the cylinder block 110. The refrigerant accommodated in the suction chamber 133 flows into the cylinder bore 111 through the suction port 141.

  The discharge hole 142 is an opening through which the discharge chamber 134 of the cylinder head 130 communicates with the cylinder bore 111 of the cylinder block 110. The refrigerant in the cylinder bore 111 flows into the discharge chamber 134 through the discharge hole 142.

  The communication hole 143 is an opening through which the discharge chamber 134 of the cylinder head 130 communicates with the communication path 116 c of the muffler 116 provided in the upper part of the cylinder block 110. The refrigerant accommodated in the discharge chamber 134 flows into the communication path 116 c through the communication hole 143.

  The crank hole 144 is an opening through which the first suction communication hole 114 of the cylinder block 110 communicates with the suction chamber 133 of the cylinder head 130. The crank hole 144 is formed in a circular shape centered on the axis of the drive shaft 150, and is formed between the second space 114 b that forms the first suction communication hole 114 and the suction chamber 133. The crank chamber 121 of the front housing 120 and the suction chamber 133 communicate with each other through a first suction communication hole 114 and a crank hole 144. Therefore, the refrigerant in the crank chamber 121 flows into the suction chamber 133 via the first suction communication hole 114 and the crank hole 144.

  The shape of the outer peripheral edge of the crank hole 144 is not limited to a circle, and may be an ellipse or a rectangle, for example. The crank hole 144 may be formed so as to at least partially overlap the suction chamber 133, and the center of the crank hole 144 may not be on the axis of the drive shaft 150. Further, a plurality of crank holes 144 may be formed. Furthermore, it is preferable that the outer peripheral edge of the crank hole 144 on the cylinder block 110 side is chamfered. As a result, even if a later-described suction valve forming plate 171 is displaced toward the suction chamber 133 due to a pressure difference between the crank chamber 121 and the suction chamber 133, the suction valve forming plate 171 is not easily damaged.

  The third discharge communication hole 145 is an opening through which the second discharge communication hole 135 of the cylinder head 130 communicates with the first discharge communication hole 115 of the cylinder block 110. The refrigerant stored in the discharge chamber 134 flows into the crank chamber 121 through the second discharge communication hole 135, the third discharge communication hole 145, and the first discharge communication hole 115.

  A drive shaft 150 is provided at the center of the cylinder block 110 and the front housing 120 so as to penetrate both. The drive shaft 150 is rotatably supported by the cylinder block 110 and the front housing 120 and is rotated by power external to the compressor 100 to reciprocate the piston 112 via the conversion mechanism 122. The drive shaft 150 is supported in the radial direction by the radial bearing 113 of the cylinder block 110 and the radial bearing 125 of the front housing 120. The drive shaft 150 is supported in the thrust direction by contacting a part of the rotor 122a with the wall surface on the opposite side of the cylinder block 110 of the crank chamber 121 via the thrust bearing 123 of the front housing 120. Movement to the opposite side of the head 130 is restricted. Further, the drive shaft 150 is supported in the thrust direction by the contacted member 170 (see FIG. 2) via the contact member 160, and is restricted from moving toward the cylinder head 130 (right side in FIG. 1).

  The drive shaft 150 includes a tilt angle decreasing spring 151, a spring support member 152, and a tilt angle increasing spring 153. The inclination reduction spring 151 is an urging means that urges the swash plate 122c until the inclination angle θ reaches the minimum inclination angle θmin. The inclination reduction spring 151 is attached to surround the outer peripheral surface of the drive shaft 150 in the crank chamber 121 of the front housing 120. An end portion of the inclination reduction spring 151 is supported by the rotor 122a and the swash plate 122c of the conversion mechanism 122. Therefore, when the inclination angle reducing spring 151 is extended, the inclination angle θ of the swash plate 122c is reduced to approach the minimum inclination angle θmin, and when the inclination angle reducing spring 151 is contracted, the inclination angle θ of the swash plate 122c is increased to the maximum inclination angle θmax. Get closer.

  The spring support member 152 is a support member that supports the end of the tilt angle increasing spring 153 on the cylinder head 130 side. The spring support member 152 is attached so as to surround the outer peripheral surface of the drive shaft 150 in the first space 114 a of the cylinder block 110. The spring support member 152 only needs to be able to support the cylinder head 130 side end portion of the inclination increasing spring 153 and may be attached to a part of the outer peripheral surface of the drive shaft 150.

  The inclination increasing spring 153 supported by the spring support member 152 is attached to surround the outer peripheral surface of the drive shaft 150 in the first space 114 a of the cylinder block 110. The end of the tilt increasing spring 153 on the cylinder head 130 side is supported by the spring support member 152, and the end on the front housing 120 side is supported by the swash plate 122c. Therefore, when the inclination increasing spring 153 is extended, the inclination angle θ of the swash plate 122c is increased to approach the maximum inclination angle θmax, and when the inclination increasing spring 153 is contracted, the inclination angle θ of the swash plate 122c is decreased to the minimum inclination angle θmin. Get closer.

  The biasing force of the tilt angle decreasing spring 151 and the tilt angle increasing spring 153 is set so that the tilt angle increasing spring 153 is larger when the tilt angle θ of the swash plate 122c is the minimum tilt angle θmin. Therefore, when the compressor 100 is stopped, that is, when the drive shaft 150 and the swash plate 122c are not rotating, the inclination angle θ is an angle θn in which the urging forces of the inclination reduction spring 151 and the inclination increase spring 153 are balanced. (Θmin <θn <θmax).

  An end 154 of the drive shaft 150 on the front housing 120 side extends through the boss portion 124 of the front housing 120 to the outside, and a power transmission device (not shown) outside the compressor 100 and a drive source (not shown). ). The drive shaft 150 is transmitted with the power of the drive source by the power transmission device, and rotates in synchronization with the rotation of the power transmission device. The end 155 of the drive shaft 150 on the cylinder head 130 side extends into the second space 114 b of the cylinder block 110.

  A contact member 160 is fixed to the end 155. The abutting member 160 is an oil separator that centrifuges the oil in the refrigerant, and is press-fitted and fixed to the end 155. The contact member 160 is formed by pressing a steel plate.

  As shown in FIG. 2, the contact member 160 includes a cylindrical portion 161, a conical portion 162, and a flange portion 163. The cylindrical portion 161 is a portion that is press-fitted into the drive shaft 150 and is formed in a cylindrical shape. The cylindrical portion 161 is formed with a plurality of suction communication holes 164 that allow communication between the inside and the outside of the contact member 160. In the second space 114 b of the cylinder block 110, the refrigerant outside the contact member 160 flows into the contact member 160 through the suction communication hole 164. With such a configuration, a suction communication path 105 described later can be easily formed.

  A frustoconical conical portion 162 that extends toward the cylinder head 130 side is formed from the end portion of the cylindrical portion 161 on the cylinder head 130 side. The suction communication hole 164 formed in the cylindrical portion 161 may be formed in the conical portion 162.

  A flange portion 163 is formed at the end of the conical portion 162 on the cylinder head 130 side. The flange portion 163 is formed in an annular shape, and abuts against the abutting portion 173 of the abutted member 170 to restrict the movement of the drive shaft 150 toward the cylinder head 130. The inner diameter of the flange portion 163 is substantially equal to or wider than the diameter of the crank hole 144 of the valve plate 140.

  The press-fitting amount of the contact member 160 with respect to the drive shaft 150 is set so that a predetermined clearance (gap) is formed between the flange portion 163 and a contact portion 173 of the contacted member 170 described later. Yes. The clearance is, for example, 50 to 150 μm. Further, the flange portion 163, the cylindrical portion 161, and the conical portion 162 are formed so that the drive shaft 150 and the axis line substantially coincide.

  In the present embodiment, the contact member 160 is fixed to the drive shaft 150 by press fitting, but may be fixed to the drive shaft 150 by other methods. Further, it may be formed integrally with the drive shaft 150. Further, the abutting member 160 is not limited to the oil separator, and any member that abuts against the abutted member 170 and restricts the axial movement of the drive shaft 150 may be used.

  As shown in FIG. 2, a contacted member 170 is provided between the cylinder block 110 and the valve plate 140. The contacted member 170 contacts the flange portion 163 of the contact member 160 and restricts the movement of the drive shaft 150 toward the cylinder head 130. In the present embodiment, the abutted member 170 includes a suction valve forming plate 171 described later. Therefore, it is not necessary to newly provide a dedicated contacted member 170, and the structure of the compressor 100 can be simplified.

  The intake valve forming plate 171 is made of, for example, a thin plate-like metal plate such as a valve strip. The suction valve forming plate 171 includes a cooling region 172, a contact portion 173, and an orifice 174.

  A cooling region 172 is set on the surface of the suction valve forming plate 171. The cooling area 172 is an area inside the contact portion 173 that contacts the flange portion 163 of the contact member 160 on the surface of the suction valve forming plate 171, and is a refrigerant accommodated in the suction chamber 133 of the cylinder head 130. It is set in the area where the pressure of In this embodiment, since the inner diameter of the flange portion 163 of the contact member 160 is formed wider than the diameter of the crank hole 144, the region where the pressure of the refrigerant accommodated in the suction chamber 133 acts is the valve plate 140. It is equal to the area inside the crank hole 144. Therefore, the outer peripheral edge of the cooling region 172 is set by the outer peripheral edge of the crank hole 144 on the suction valve forming plate 171 side. With such a configuration, the outer peripheral edge of the cooling region 172 can be easily set.

  Since the pressure of the low-temperature refrigerant stored in the suction chamber 133 acts on the cooling region 172, the cooling region 172 and the surrounding region, that is, the contact portion 173 can be cooled. In particular, in the present embodiment, the cooling region 172 is set in the entire region inside the contact portion 173, so that the contact portion 173 can be efficiently cooled.

  Further, since the inner diameter of the flange portion 163 is substantially equal to or wider than the diameter of the crank hole 144, the plate portion of the valve plate 140 abuts on the cylinder head 130 side of the abutting portion 173. That is, the contact portion 173 is supported by the valve plate 140 on the entire circumference. Therefore, the contact portion 173 does not deform even when the flange portion 163 contacts, and can stably support the contact member 160 (drive shaft 150).

  An orifice 174 is formed at the center of the cooling region 172 of the intake valve forming plate 171 coaxially with the axis of the drive shaft 150. The orifice 174 is an opening through which the first suction communication hole 114 of the cylinder block 110 and the suction chamber 133 of the cylinder head 130 communicate with each other. The refrigerant in the contact member 160 passes through the orifice 174 and passes through the cylinder head. It flows into 130 suction chambers. With such a configuration, a suction communication path 105 described later can be easily formed. The orifice 174 may not be formed coaxially with the axis of the drive shaft 150.

  The intake valve forming plate 171 includes an intake valve (not shown). This suction valve is a valve that controls the inflow of refrigerant from the suction chamber 133 of the cylinder head 130 to the cylinder bore 111 of the cylinder block 110. The suction valve is formed on the suction hole 141 of the valve plate 140. The refrigerant accommodated in the suction chamber 133 of the cylinder head 130 flows into the cylinder bore 111 of the cylinder block 110 through this suction valve.

  As shown in FIG. 2, a discharge valve forming plate 175 is provided between the cylinder head 130 and the valve plate 140. The discharge valve forming plate 175 is made of, for example, a thin metal plate such as a valve strip steel. The discharge valve forming plate 175 includes a crank hole 176.

  The crank hole 176 is an opening through which the first suction communication hole 114 of the cylinder block 110 communicates with the suction chamber 133 of the cylinder head 130. The crank hole 176 is provided at the center of the discharge valve forming plate 175 and is preferably formed in the same position and in the same shape as the crank hole 144 of the valve plate 140.

  The discharge valve forming plate 175 includes a discharge valve (not shown). This discharge valve is a valve that controls the inflow of refrigerant from the cylinder bore 111 of the cylinder block 110 to the discharge chamber 134 of the cylinder head 130. The discharge valve is formed on the discharge hole 142 of the valve plate 140. The refrigerant compressed in the cylinder bore 111 flows into the discharge chamber 134 through this discharge valve.

  Further, the compressor 100 includes a cylinder gasket 102 between the cylinder block 110 and the suction valve forming plate 171, and a head gasket 103 between the discharge valve forming plate 175 and the cylinder head 130. Thereby, it is possible to prevent the refrigerant from leaking between the cylinder block 110 and the intake valve forming plate 171 and between the discharge valve forming plate 175 and the cylinder head 130. In the head gasket 103, a crank hole having the same shape as the crank hole 176 formed in the discharge valve forming plate 175 is formed at the same position as the crank hole 17.

  Furthermore, the compressor 100 includes a center gasket (not shown) between the front housing 120 and the cylinder block 110. Thereby, the leakage of the refrigerant from between the front housing 120 and the cylinder block 110 can be prevented.

  The cylinder gasket 102, the head gasket 103, and the center gasket each have an opening so as not to obstruct the refrigerant flow path formed in the compressor 100.

  The cylinder block 110, the front housing 120, the cylinder head 130, the valve plate 140, the suction valve forming plate 171, the discharge valve forming plate 175, the cylinder gasket 102, the head gasket 103, and the center gasket described above are bolts formed coaxially. Has holes. The above members are fastened through bolts 101 to these bolt holes to form the housing of the compressor 100. It is preferable that a plurality of bolt holes are formed on the outer peripheral portion of the compressor 100.

Next, the operation of the compressor 100 configured as described above will be described with reference to FIGS. 1 and 2.
When the compressor 100 is operated, the drive shaft 150 is rotated by the drive source. As the drive shaft 150 rotates, the swash plate 122c rotates, causing the piston 112 to reciprocate via the shoe 112b. A compression reaction force in the direction from the cylinder head 130 side to the front housing 120 side acts on the piston 112. For this reason, the drive shaft 150 is pressed toward the front housing 120 side. The rotor 122 a fixed to the drive shaft 150 abuts against the wall surface of the crank chamber 121 opposite to the cylinder block 110 via the thrust bearing 123. As a result, the movement of the drive shaft 150 toward the front housing 120 is restricted.

  Thus, when the rotor 122a is in contact with the wall surface of the crank chamber 121, a predetermined clearance is formed between the flange portion 163 of the contact member 160 and the contact surface of the suction valve forming plate 171.

  A relatively low temperature suction refrigerant flows into the suction chamber 133 of the cylinder head 130 from the external refrigerant circuit through the suction port 131 and the communication path 132. The refrigerant flowing in is accommodated in the suction chamber 133 and flows into the cylinder bore 111 through the suction hole 141 of the valve plate 140 and the suction valve of the suction valve forming plate 171 as the piston 112 moves.

  The refrigerant flowing into the cylinder bore 111 is compressed by the piston 112 and flows into the discharge chamber 134 of the cylinder head 130 through the discharge hole 142 of the valve plate 140 and the discharge valve of the discharge valve forming plate 175.

  The refrigerant flowing into the discharge chamber 134 is accommodated in the discharge chamber 134, and when the pressure in the discharge chamber 134 (and the communication path 116c of the muffler 116) and the muffler space 116e becomes larger than a predetermined value, the check valve 116d opens. . When the check valve 116d is opened, the refrigerant stored in the discharge chamber 134 flows into the muffler space 116e through the communication hole 143, the communication path 116c, and the check valve 116d of the valve plate 140. The refrigerant flowing into the muffler space 116e is discharged from the discharge port 116f to an external refrigerant circuit.

  A part of the refrigerant stored in the discharge chamber 134 is not discharged to the external refrigerant circuit as described above, but flows into the crank chamber 121 of the front housing 120 through the discharge communication path 104. When the refrigerant flows into the crank chamber 121, each part in the crank chamber 121 is lubricated by oil contained in the refrigerant.

  The amount of refrigerant flowing into the crank chamber 121 is controlled by the control valve 136. The opening degree of the control valve 136 is controlled by controlling the energization amount to the built-in solenoid by an external signal. When the opening degree of the control valve 136 increases, the amount of refrigerant flowing into the crank chamber 121 increases, the pressure in the crank chamber 121 increases, the inclination angle θ of the swash plate 122c decreases, and the stroke (reciprocation) of the piston 136 increases. The length of motion) is shortened, and the refrigerant discharge capacity from the compressor 100 is reduced. Conversely, when the opening degree of the control valve 112 decreases, the amount of refrigerant flowing into the crank chamber 121 decreases, the pressure in the crank chamber 121 decreases, the inclination angle θ of the swash plate 122c increases, and the piston 112 The stroke becomes longer and the discharge capacity of the refrigerant from the compressor 100 increases. Thus, the control valve 136 can control the discharge capacity of the refrigerant from the compressor 100.

  The refrigerant flowing into the crank chamber 121 flows into the first suction communication hole 114 of the cylinder block 110, the suction communication hole 164 of the contact member 160, the orifice 174 of the suction valve forming plate 171, and the crank hole 144 of the valve plate 140. Then, the air flows into the suction chamber 133 through the suction communication passage 105 including the crank hole 176 of the discharge valve forming plate 175 and the crank hole formed in the head gasket 103. At this time, the oil contained in the refrigerant lubricates between the flange portion 163 of the contact member 160 and the contact portion 173 of the suction valve forming plate 171. Therefore, the slidability between the flange part 163 and the contact part 173 can be improved. The oil contained in the refrigerant is centrifuged by the contact member 160. Thereby, the amount of oil contained in the refrigerant discharged to the external refrigerant circuit can be reduced.

  When the compressor 100 is stopped, the energization to the solenoid built in the control valve 136 is stopped, the control valve 136 is fully opened, the pressure in the crank chamber 121 is rapidly increased, and the inclination angle θ of the swash plate 122c is minimized. The inclination angle θmin. At this time, the back pressure of the piston 112 increases due to the increased pressure in the crank chamber 121. When the back pressure exceeds the compression reaction force that presses the drive shaft 150 toward the front housing 120, the drive shaft 150 is pressed toward the cylinder head 130, and the rotating contact with the contact portion 173 of the intake valve forming plate 171. The flange part 163 of the member 160 may contact | abut.

  Even in such a case, the cooling region 172 of the suction valve forming plate 171 is cooled by the refrigerant accommodated in the suction chamber 133, and the contact portion 173 located outside the cooling region 172 is also cooled by heat conduction. Therefore, the temperature rise of the contact part 173 can be suppressed. Thereby, even when the lubrication at the contact portion 173 is insufficient, the occurrence of seizure at the contact portion can be suppressed. In particular, since the intake valve forming plate 171 is a metal thin plate, it has high thermal conductivity and can efficiently suppress the temperature rise of the contact portion 173.

FIG. 3 is an enlarged cross-sectional view of a main part showing a second embodiment of the compressor according to the present invention.
In the present embodiment, the diameter of a part of the crank hole 144 of the valve plate 140 is formed wider than the inner diameter of the flange portion 163 of the contact member 160. With such a configuration, the pressure of the refrigerant accommodated in the suction chamber 133 also acts on part of the contact part 173 and part of the external region 177 outside the contact part 173. In this case, the cooling region 172 is a region obtained by adding a part of the contact portion 173 and the external region 177 to the cooling region 172 in the first embodiment. Therefore, the area of the cooling region 172 is larger than that in the first embodiment, and the temperature rise of the contact portion 173 can be more efficiently suppressed.

FIG. 4 is an essential part enlarged sectional view showing a third embodiment of the compressor according to the present invention.
In the present embodiment, the contacted member 170 includes a discharge valve forming unit 175. As shown in FIG. 4, the crank hole 144 of the valve plate 140 is formed to be larger than the outer diameter of the flange portion 163 of the contact member 160. The crank hole 144 is formed in the same shape and at the same position as the opening of the second space 114 b of the cylinder block 110. In addition, an opening having the same shape as the crank hole 144 is formed at the same position as the crank hole 144 at the center of the intake valve forming plate 171 and the cylinder gasket 102.

  An orifice 178 is formed substantially coaxially with the axis of the drive shaft 150 at the center of the discharge valve forming plate 175. Further, a circular opening 106 having a diameter equal to the inner diameter of the flange portion 163 of the contact member 160 is formed at the center of the head gasket 103. With such a configuration, the contact portion 173 can be supported by the head gasket 103.

  Further, in the present embodiment, the cylinder head 130 includes a plurality of ribs 107. The rib 107 extends from the wall surface of the cylinder head 130 and is formed to support the contact portion 173 via the head gasket 103. With such a configuration, the contact portion 173 can be supported by the rib 107. In the present embodiment, the suction communication passage 105 includes the first suction communication hole 114 of the cylinder block 110, the suction communication hole 164 of the contact member 160, the orifice 178 of the discharge valve forming plate 175, and the head gasket 103. And an opening 106.

FIG. 5 is a sectional view showing a fourth embodiment of the compressor according to the present invention.
In the present embodiment, the drive shaft 150 includes a second suction communication hole 156. As shown in FIG. 5, the second suction communication hole 156 communicates the space where the shaft seal device 126 of the boss portion 124 of the front housing 120 is disposed with the second space 114 b of the cylinder block 110.

  The refrigerant in the crank chamber 121 of the front housing 120 includes a communication passage 127 of the boss portion 124, a second suction communication hole 156, an orifice 174 of the suction valve forming plate 171, a crank hole 144 of the valve plate 140, and a discharge valve. The air flows into the suction chamber 133 of the cylinder head 130 through the suction communication passage 105 including the crank hole 176 of the forming plate 175 and the crank hole of the head gasket 103.

  In addition, as shown in FIG. 6, a part of the flange portion 163 of the contact member 160 communicates with the inside and the outside of the contact member 160 by providing a space between the contact portion 173 and the flange portion 163. A passage 165 is formed. Note that the suction communication hole 164 formed in the first to third embodiments is not formed.

  With such a configuration, the refrigerant flowing into the second space 114b of the cylinder block 110 through the suction communication passage 105 is subjected to centrifugal separation of the oil by the rotation of the contact member 160, and the separated oil is separated from the communication passage 165 and the first passage. The refrigerant is returned to the crank chamber 121 through the suction communication hole 114. Therefore, it is possible to secure a sufficient amount of oil in the crank chamber 121 when the compressor 100 is in operation. Moreover, the outflow of oil to the external refrigerant circuit can be reduced.

  As mentioned above, although embodiment of this invention was described in detail based on the accompanying drawing, the compressor 100 by this invention is not restricted to said structure, For example, the cooling area | region 172 of the to-be-contacted member 170 is provided with a rib. May be. By increasing the surface area of the cooling region 172 by the rib, the contact portion 173 can be cooled more effectively.

  Further, the abutted member 172 may be a metal plate, and is not limited to the suction valve forming plate 171 and the discharge valve forming plate 175. For example, a new metal plate different from the suction valve forming plate 171 and the discharge valve forming plate 175 may be brought into contact with the flange portion 163 of the contact member 160 as the contacted member 172.

  The compressor 100 according to the present invention is not limited to a clutchless compressor, and may be, for example, a compressor using an electromagnetic clutch or a motor-driven compressor.

DESCRIPTION OF SYMBOLS 100 ... Compressor, 101 ... Bolt, 102 ... Cylinder gasket, 103 ... Head gasket, 104 ... Discharge communication path, 105 ... Suction communication path, 106 ... Opening, 107 ... Rib, 110 ... Cylinder block, 111 ... Cylinder bore, 112 ... piston, 112a ... end of piston on the front housing side, 112b ... shoe, 113 ... radial bearing, 114 ... first suction communication hole, 114a ... first space, 114b ... second space, 114c ... communication hole, 115 ... 1st discharge communication hole, 116 ... muffler, 116a ... lid member, 116b ... wall portion, 116c ... communication path, 116d ... check valve, 116e ... muffler space, 116f ... discharge port, 120 ... front housing, 121 ... crank chamber 122a conversion mechanism 122a rotor 122b link mechanism 122c swash plate 122h ... through hole, 122i ... maximum tilt angle restricting portion, 122j ... minimum tilt angle restricting portion, 122p ... first arm, 122q ... second arm, 122r ... link arm, 122s ... first connecting pin, 122t ... second connecting pin, DESCRIPTION OF SYMBOLS 123 ... Thrust bearing, 124 ... Boss part, 125 ... Radial bearing, 126 ... Shaft seal device, 127 ... Communication path, 130 ... Cylinder head, 131 ... Suction port, 132 ... Communication path, 133 ... Suction chamber, 134 ... Discharge chamber , 135 ... second discharge communication hole, 136 ... control valve, 140 ... valve plate, 141 ... suction hole, 142 ... discharge hole, 143 ... communication hole, 144 ... crank hole, 145 ... third discharge communication hole, 150 ... drive Shaft, 151... Tilt decreasing spring, 152. Spring support member, 153. Tilt increasing spring, 154. End of drive shaft on front housing side, 155. End of the shaft on the cylinder head side, 156... Second suction communication hole, 160 ... contact member, 161 ... cylindrical part, 162 ... conical part, 163 ... flange part, 164 ... suction communication hole, 165 ... communication path, 170 ... abutted member, 171 ... suction valve forming plate, 172 ... cooling region, 173 ... contact portion, 174 ... orifice, 175 ... discharge valve forming plate, 176 ... crank hole, 177 ... outer region, 178 ... orifice

Claims (5)

A cylinder block in which a plurality of cylinder bores are defined;
A front housing attached to one end side of the cylinder block and formed with a crank chamber;
A cylinder head that is attached to the other end of the cylinder block and includes a suction chamber that stores the refrigerant sucked from the refrigerant circuit and a discharge chamber that stores the refrigerant discharged to the refrigerant circuit;
A valve plate provided between the cylinder block and the cylinder head and formed with a suction hole for communicating the cylinder bore and the suction chamber, and a discharge hole for communicating the cylinder bore and the discharge chamber;
A suction valve forming plate provided between the cylinder block and the valve plate, and formed with a suction valve that allows the refrigerant to flow into the cylinder bore from the suction chamber via the suction hole;
A discharge valve forming plate provided between the valve plate and the cylinder head and formed with a discharge valve that allows discharge of refrigerant from the cylinder bore to the discharge chamber via the discharge hole;
A drive shaft rotatably supported by the cylinder block and the front housing;
A contact member fixed to an end of the drive shaft on the cylinder head side;
A contacted member that is provided between the cylinder block and the cylinder head and that contacts the contact member and restricts movement of the drive shaft toward the cylinder head;
Pistons disposed in the plurality of cylinder bores;
A conversion mechanism for converting the rotation of the drive shaft into a reciprocating motion of the piston;
In the compressor with
The abutting surface of the abutting member that abuts on the abutted member is formed in an annular shape, and the drive shaft side of the area inside the abutting portion with which the abutting surface abuts out of the surface of the abutted member An area where the pressure of the refrigerant accommodated in the suction chamber acts is set on at least a part of the surface opposite to the compressor.   An outer peripheral edge of a region where the pressure of the refrigerant accommodated in the suction chamber acts is provided between the abutted member and the suction chamber of the cylinder head, and a member disposed adjacent to the abutted member. The compressor according to claim 1, wherein the compressor is set by an outer peripheral edge of the through hole.   3. The compressor according to claim 2, wherein the contacted member includes one of the suction valve forming plate and the discharge valve forming plate. The contacted member is the suction valve forming plate,
The outer peripheral edge of the region where the pressure of the refrigerant accommodated in the suction chamber acts is set by the outer peripheral edge of a through hole formed in the valve plate and connected to the suction chamber. The compressor described.   The through hole formed in the valve plate is formed in a circle substantially coaxial with the axis of the drive shaft, and the diameter of the through hole is set to be substantially equal to the inner diameter of the contact surface of the contact member. The compressor according to claim 4.

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