JPH07293437A - Variable displacement swash plate type compressor - Google Patents

Abstract

PURPOSE:To provide a variable volume tilting plate type compressor which enables operation under a complete distroke state, has small size, light weight, brings about a small cost. CONSTITUTION:In a variable volume tilting plate type compressor, a moving means 52 forcibly moves in an axial direction a sleeve 61 until inclination of a socket plate 16 is shifted from a position perpendicular to a driving shaft 11 to a position inclined by a specified angle, which sleeve 61 is slidably fitted to the driving shaft 11 in an axial direction, and with which the socket plate 16 is oscillatably engaged through a connecting pin 64. The moving means 52 a push pin 62 which is abutted against an axial end face of the sleeve 61 in a reciprocating manner in an axial direction, and a hydraulic mechanism 63 which applies hydraulic pressure to the push pin 62 for moving.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a variable capacity swash plate type compressor in which the amount of discharged refrigerant is adjusted according to the pressure state of return refrigerant.

[0002]

2. Description of the Related Art As a compressor used in a recent automobile air conditioner, a variable displacement swash plate type compressor as shown in FIG. 5 has been proposed (for example, Japanese Patent Laid-Open No. 58-58).
158,382).

The variable displacement swash plate compressor 3 adjusts the amount of refrigerant discharged from the compressor 3 by changing the volume of the compression chamber in the cylinder 25 in accordance with the suction pressure of the refrigerant returned to the compressor. Is to be constant.

When the suction pressure is made constant in this way, the refrigerant pressure at the outlet of the evaporator (that is, the evaporation pressure of the refrigerant in the evaporator) becomes constant to some extent, and it is possible to avoid so-called evaporator freezing at low load. Become.

The variable displacement swash plate compressor 3 has a drive shaft 11 which is rotationally driven by an engine via a belt, a pulley 2 and a magnet clutch 2a. A drive rod 11a is provided on the drive shaft 11 so as to project in a direction perpendicular to the shaft 11 so as to rotate together with the drive shaft 11 in the crank chamber 12.

A drive swash plate 13 is connected to the drive rod 11a so as to be tiltable and swingable with respect to the drive shaft 11 with a pin 11b as a fulcrum, and the rotational force of the drive shaft 11 is applied to the drive rod 11.
It is adapted to be transmitted to the drive swash plate 13 via a and the pin 11b. The drive swash plate 13 has a thrust bearing 1
A non-rotating socket plate 16 is slidably mounted via the shaft 4 and the radial bearing 15.

The socket plate 16 has a shoe 19 slidably connected to a guide pin 18 fixed to a casing 17 of the crank chamber 12. The shoe 19 prevents rotation of the shoe, while the shoe 19 prevents the socket plate 16 from rotating in the axial direction. The reciprocating motion of is allowed. A plurality of piston rods 22 are attached to the socket plate 16 via spherical bearings 22a at equal intervals in the circumferential direction.
A piston 23 is connected to the other end of the through a spherical bearing 22b.

The rotation of the drive swash plate 13 causes the socket plate 16 to reciprocate in the axial direction by performing a so-called rasping operation, which causes the piston 23 to reciprocate via the piston rod 22. The front side portion of the piston 23 of the cylinder 25 into which the piston 23 is inserted is in communication with the compression chamber, and the rear side portion thereof is in communication with the crank chamber 12.

The cylinder head 30 is provided with a suction port 29 and a discharge port 33, and the suction port 29 is
This is the part into which the return refrigerant from the evaporator flows, and this refrigerant flows into the cylinder bore 26 against the closing repulsive force of the suction valve 34 that closes the suction port 27 opened in the valve plate 20. There is. Further, this refrigerant is introduced into the suction side pressure chamber 32 through a communication passage 32a communicating with the suction port 29 formed in the cylinder head 30.

On the other hand, the discharge port 33 is a portion through which the compressed refrigerant flows out, and a pipe (not shown) for sending the refrigerant discharged from the discharge port 28 formed in the valve plate 20 to the condenser. It communicates with the discharge side pressure chamber 35 through a communication passage 35a.

The suction side pressure chamber 32 and the discharge side pressure chamber 35
A control valve Cv is provided between the control valve Cv and the control valve Cv, and the control valve Cv has a first control valve 36 at the bottom and a second control valve 39 at the top.
Is a bellows 37 that expands and contracts according to the internal pressure of the suction side pressure chamber 32, and a spring 38 provided in the bellows 37.
The opening degree of the first valve port 40 is adjusted by the balance of the force of
1, the through hole 42, the passage 43, the center hole 44 of the cylinder 25, and the passage 45 of the drive shaft 11 to guide the crank chamber 12.

The first control valve 36 has an operating rod 46.
Is provided, and the operating rod 46 allows the second control valve 39
Is to be opened. And both control valves 3
Since 6, 6 and 39 operate in conjunction with each other, when the first control valve 36 increases the opening degree of the first valve opening 40 as described above, the second control valve 39 is the second valve. Mouth 47
Can be operated so as to reduce the opening degree of.

Therefore, when the heat load in the cooling cycle is small, the pressure of the return refrigerant does not have a sufficient amount of superheat and returns at a low pressure.
The pressure in 2 decreases, the bellows 37 extends upward, the second valve port 47 is wide open, and the high-pressure refrigerant compressed by the piston 23 in the compression process is discharged from the discharge port 28 through the second valve port 47. Crank chamber 12 through 48, 49
To increase the internal pressure of the crank chamber 12.

Therefore, the inclination angle of the socket plate 16 is controlled by the pressure balance before and after being applied to the plurality of pistons 23. That is, when the pressure in the crank chamber 12 becomes slightly larger than the pressure on the suction side, the combined force of the forces applied to the back surfaces of the plurality of pistons 23 acts as a moment about the pin 11b of the socket plate 16, and this socket plate 16 Acts to reduce the tilt angle of.

Therefore, the piston 23 in the suction process
Cannot retreat by a sufficient stroke, and can perform only a small compression stroke when entering the next compression step, which reduces the amount of refrigerant compression, the amount of discharged refrigerant, and the refrigerant flow rate circulating in the cooling cycle. Is reduced, and the amount of refrigerant is appropriate according to the low heat load. Due to the decrease in the amount of the refrigerant, the suction pressure of the compressor 3 gradually increases, and as a result, the suction pressure is kept constant.

When the heat load in the cooling cycle is large, the pressure in the suction side pressure chamber 32 becomes high, the bellows 37 contracts, and the first control valve 36 moves downward.
Since the opening degree of the first valve opening 40 is large and the opening degree of the second valve opening 47 is small and the suction pressure is introduced into the crank chamber 12, the internal pressure thereof becomes substantially equal to the suction pressure.

Therefore, even in the piston 23 in the suction process, there is almost no pressure difference between the front and the rear, and the piston 23 can be smoothly retracted in the bore 26 of the cylinder 25. The socket plate 16 and the drive swash plate 13 are easily tilted to the maximum with respect to the drive shaft 11 due to the reaction force of the compression force, and the reciprocating stroke of the piston 23 is lengthened. Therefore, if compression is performed in this state, the amount of discharged refrigerant increases, the flow rate of the refrigerant circulating in the cooling cycle increases, and the flow rate of the refrigerant becomes appropriate according to the high heat load.
The suction pressure of is gradually decreased, and as a result, the suction pressure is kept constant.

[0018]

By the way, in the variable displacement swash plate compressor 3 as described above, the compression capacity is 0 (zero) structurally, that is, the socket plate 16 is used.
The inclination of can be set to a state perpendicular to the drive shaft 11 (hereinafter, also referred to as a complete destroke). However, once the complete destroke is completed, the pressure difference before and after the piston 23 disappears and the socket plate 16 Also, the drive swash plate 13 cannot be tilted again, and it is necessary to avoid this.

That is, when starting the compressor, the piston 2
Since the back pressure of 3 is no longer obtained, the return spring 5
0 is provided, and the return spring 50 elastically repels the drive swash plate 13 and the like so that a predetermined tilted state is obtained, so that the amount of discharged refrigerant at the time of startup is not zero.

However, in the conventional variable displacement swash plate type compressor 3, as long as the drive shaft 11 is rotated by the rotation of the engine, as described above, at least the drive swash plate 13 and the like are in a predetermined inclined state by the return spring 50. Since the operation is performed with a constant discharge refrigerant amount that matches this inclination, the refrigerant always circulates in the cooling cycle even when it is not necessary, and wasteful work is forced. Therefore, there is a problem that an extra load is applied to the engine, resulting in a reduction in fuel consumption of the vehicle and a risk of freezing of the evaporator.

On the other hand, there is one in which an operating rod is connected to the outer peripheral end of the socket plate 16 on the side opposite to the pin 11b, and the operating rod is retracted by a solenoid to forcibly perform a complete destroke. (JP-A-63-1
(See Japanese Patent No. 83277), the drive swash plate and the like are brought into a predetermined tilt state by the return spring at the time of starting the compressor, and the solenoid must be always turned on at the time of complete destroke. Moreover, since the stroke of the actuating rod is large and a considerable pressing force is required, the capacity of the solenoid must be increased to a predetermined value or more, and the solenoid itself and the compressor as a whole are increased in size.

The present invention has been made in view of the above problems of the prior art, and an object of the present invention is to enable operation in a complete destroke state, and to reduce the size and weight of the variable variable tilt. It is to provide a plate compressor.

[0023]

SUMMARY OF THE INVENTION To achieve the above object, the present invention relates to a socket plate which is variably connected to a drive shaft and whose inclination angle is variable, and which reciprocates in the axial direction by rotation of the drive shaft. The crank, which has a piston connected to the socket plate and a cylinder in which the piston slides in the crank chamber, acts on the back surface of the piston according to the pressure of the refrigerant returning to the suction port of the cylinder. In a variable displacement compressor provided with a control valve for controlling the tilt angle by adjusting the pressure in the room, the compressor is slidably fitted onto the drive shaft in the axial direction, and the socket plate swings around a predetermined point. The movably engaged sleeve is moved to a position where the socket plate is inclined at a predetermined angle from the position where the inclination of the socket plate is perpendicular to the drive shaft. A variable capacity swash plate type compressor, characterized in that a moving means for forcibly moved in the axial direction.

Further, the moving means has a rod provided in contact with an axial end surface of the sleeve so as to be movable back and forth in the axial direction, and a hydraulic mechanism portion for applying hydraulic pressure to the rod to move the rod. It is good to configure as follows.

[0025]

In the present invention thus constructed, the socket plate can be easily tilted from the upright state by moving the sleeve in the axial direction by the moving means. That is, by making a complete destroke,
Even if the drive shaft is rotated, no refrigerant is discharged from the compressor, which is a so-called inoperative state. On the other hand, it is possible to forcibly incline the socket plate by the moving means at startup. As a result, it is possible to prevent the refrigerant from constantly circulating in the cooling cycle with a predetermined minimum discharge amount and forced to useless work even when it is not necessary as in the conventional case.

Further, since the so-called inoperative state can be achieved without using the clutch, the clutch itself can be eliminated and the structure of the compressor becomes extremely simple. For this reason, workability at the time of assembling the compressor is improved, which is advantageous in terms of cost, is significantly reduced in weight, and is further improved in fuel efficiency of the vehicle.

Further, since the rod, which is brought into contact with the axial end face of the sleeve and is movable back and forth in the axial direction, is moved by the hydraulic pressure applied by the hydraulic mechanism portion, the rod has a compact structure and sufficient pressing force. Is obtained.

[0028]

Embodiments of the present invention will be described below with reference to the drawings. 1 is a schematic cross-sectional view showing a piston discharge process in a variable displacement swash plate compressor according to an embodiment of the present invention, FIG. 2 is a perspective view showing a push pin shown in FIG. 1, and FIG. 4A is a cross-sectional view taken along the line AA in FIG. 4, FIG. 4A is a schematic view showing a complete disstroke state in which the socket plate is upright, and FIG. 4B is a diagram in which the sleeve is moved by the push pin. It is a figure which shows typically the state which made the socket plate incline, and attaches | subjects the same code | symbol to the member common to the member shown in FIG. 5, and abbreviate | omits the description.

Variable capacity swash plate compressor 5 of this embodiment
As shown in FIG. 1, the reference numeral 1 has a drive swash plate 13 which is connected to a drive shaft 11 in a variable inclination angle. A sleeve 61 is fitted into the drive shaft 11, and the sleeve 61 is connected to the drive swash plate 13 via a pair of left and right connecting pins 64 and interlocks with the swing of the drive swash plate 13. It is configured to be slidable in the axial direction.

In this embodiment, in particular, the sleeve 61 is
A moving means 52 for forcibly moving the drive swash plate 13 and the socket plate 16 connected to the drive shaft 11 in the axial direction from a position at which the drive shaft 11 is inclined at a right angle to the drive shaft 11 is provided. ing. In FIG. 1, the control valve Cv, the passage of the refrigerant, etc. are simplified or omitted in order to avoid complication of the drawing.

As shown in FIG. 1, the moving means 52 is in contact with the axial end surface of the sleeve 61 and is provided with a push pin 62 which is movable forward and backward in the axial direction of the drive shaft 11 and the push pin 62. The pin 62 has a hydraulic mechanism 63 for applying hydraulic pressure to move the pin 62 in the direction of the sleeve 61.

As shown in FIG. 2, the push pin 62 is provided with a disc-shaped pressure receiving plate 66 at one end of a shaft portion 65, and is supplied to the pressure receiving plate 66 from the hydraulic mechanism portion 63. Hydraulic pressure is applied, and the push pin 62 itself can be moved toward the sleeve 61. On the other hand, a rod-shaped contact portion 67 is joined to the other end so that the shaft portion 65 and the axis line are orthogonal to each other so as to have a T-shape.

The push pin 62 is provided coaxially with the drive shaft 11 at the left end in the figure, and the drive shaft 11 has a guide portion into which the shaft portion 65 of the push pin 62 is axially movable. Abutment portion 6 of hole 68 and push pin 62
An elongated hole 69 is formed so that 7 can be moved back and forth in the axial direction. As a result, as shown in FIG.
The vicinity of both ends of the contact portion 67 of the push pin 62 is brought into contact with the end surface of the sleeve 61, and the sleeve 61 can be moved in the axial direction. In addition, the abutting portion 67 extends only one side with respect to the shaft portion 65, and
You may combine so that it may exhibit a character shape.

A spring member 70 is provided which abuts against the back surface of the pressure receiving plate 66 of the push pin 62.
The push pin 62 is normally elastically urged to the left in the drawing by the spring member 70, so that the contact portion 67 of the push pin 62 is located at a position slightly separated from the sleeve 61 by a predetermined distance. It is set.

As shown in FIG. 1, the hydraulic mechanism section 63 includes a hydraulic pump 71 for generating a predetermined hydraulic pressure applied to the end surface of the pressure receiving plate 66 of the push pin 62,
It is composed of a solenoid valve 72 and the like for controlling the additional direction of the hydraulic pressure generated by the hydraulic pump 71.

A gear pump, for example, is used as the hydraulic pump 71, and a predetermined hydraulic pressure can be obtained by rotating the drive shaft 11. An oil hole 73 communicating with the discharge part of the hydraulic pump 71 is provided, and when hydraulic pressure is not supplied to the push pin 62, it is released to an oil sump 78 below via a solenoid valve 72. On the other hand, an oil hole 74 for supplying hydraulic pressure to the push pin 62 from the oil hole 73 via the electromagnetic valve 72, and a relief hole 75 are provided.

The solenoid valve 72 has an operating rod 76 inserted in a valve hole 77 so as to be able to move back and forth. The direction in which the hydraulic pressure is applied can be switched depending on the axial position of the operating rod 76. That is, when the solenoid valve 72 is in the off state,
The actuating rod 76 is at the maximum protruding position by a spring member or the like (not shown), and the oil discharged from the hydraulic pump 71 is guided to the oil sump 78 through the passage 76a. On the other hand, when the solenoid valve 72 is turned on, the operating rod 76 retracts axially rearward to the minimum protruding position, and the discharge oil from the hydraulic pump 71 is guided to the end surface of the pressure receiving plate 66 of the push pin 62 through the passage 76b. Then, the push pin 62 presses the sleeve 61 to incline the drive swash plate 13 and the socket plate 16 with respect to the drive shaft 11. It is also possible to use a part of the discharged oil for other purposes such as forced lubrication of the bearing, and the configurations of the oil hole circuit and the solenoid valve 72 are not limited to the above configurations.

Next, the operation of this embodiment will be described. When the drive shaft 11 rotates using the engine as a drive source, the drive rod 11a and the drive swash plate 13 rotate accordingly. Since the drive swash plate 13 is inclined with respect to the drive shaft 11, the drive swash plate 13 turns in a rasping motion. Along with this, the non-rotating socket plate 16 also reciprocates, and the refrigerant is sucked, compressed, and discharged by the operation of the piston 23.

Here, when the heat load in the cooling cycle is small, the pressure of the return refrigerant is not sufficient to obtain a superheat amount, and the refrigerant is returned at a low pressure. In this case, the solenoid valve 72
Is in the off state, the hydraulic pressure from the hydraulic pump 71 is released without being added to the push pin 62, and the high pressure refrigerant compressed by the piston 23 in the compression process is introduced into the crank chamber 12 by the action of the control valve Cv. The internal pressure of the crank chamber 12 is increased.

As a result, the pressure balance before and after being applied to the plurality of pistons 23 becomes different, and the combined force of the forces applied to the back surfaces of the plurality of pistons 23 acts as a moment about the pin 11b of the socket plate 16, and this socket The inclination angle of the plate 16 will be reduced.

Here, in this embodiment, since it is structurally allowed that the inclination angle of the socket plate 16 is decreased and the socket plate 16 is in the upright state, complete destroke is possible. For this reason, even if it is not necessary, it is possible to prevent the refrigerant from constantly circulating in the cooling cycle and forcing unnecessary work. Therefore, an unnecessary load is not applied to the engine, and as a result, the fuel efficiency of the vehicle can be reduced. Furthermore, the risk of evaporator freezing is avoided.

On the other hand, when the heat load in the cooling cycle is large, unlike the case described above, the suction pressure is introduced into the crank chamber 12 by the action of the control valve Cv, so that the internal pressure is almost equal to the suction pressure. Become.

Therefore, even in the piston 23 in the suction process, the pressure difference between the front and the rear is almost eliminated, and the piston 23 can be smoothly retracted in the bore 26 of the cylinder 25. However, here, when the socket plate 16 is in the upright state and is completely destroked, the piston 23 does not reciprocate, so the reaction force of the compression force of the piston 23 does not act, and the socket plate 16 is in the upright state. It cannot be tilted as it is (see FIG. 4 (a)).

In this embodiment, in this case, the solenoid valve 72 is turned on, and the oil discharged from the hydraulic pump 71 is guided to the end surface of the pressure receiving plate 66 of the push pin 62 through the passage 76b. Thus, as shown in FIG. 4B, hydraulic pressure is applied to the push pin 62 in the direction of the arrow to move the push pin 62, thereby pressing the sleeve 61 to move the drive swash plate 13 and the socket plate 16 to the drive shaft 11. Tilt against.

As described above, when the drive swash plate 13 is inclined even slightly, the reaction force of the compression force of the piston 23 in the compression process acts on the drive swash plate 13 so that the socket plate 16 and the drive can be easily driven. Since the swash plate 13 is inclined with respect to the drive shaft 11, the reciprocating stroke of the piston 23 becomes long. Therefore, if compression is performed in this state, the amount of discharged refrigerant increases, the flow rate of the refrigerant circulating in the cooling cycle increases, and the refrigerant flow rate becomes appropriate according to the heat load, and the suction pressure of the compressor gradually decreases. It will be maintained at a constant suction pressure. After that, the solenoid valve 72
Turn on the socket plate 16 according to the change of heat load.
To allow tilting.

In the full stroke state, that is, when the drive swash plate 13 is tilted to the maximum and the compressor is continuously operated, the solenoid valve 72 is turned on and the sleeve 61 is turned on.
Is pressed to forcibly tilt the drive swash plate 13 and the like.

As described above, in the variable capacity swash plate type compressor 51 of this embodiment, the socket plate 16 has the connecting pin 6.
The sleeve 61, which is swingably engaged via the shaft 4, is forcibly moved in the axial direction from a complete destroke position where the inclination of the socket plate 16 is perpendicular to the drive shaft 11 to a position where it is inclined by a predetermined angle. Since the moving means 52 is provided, the socket plate 16 can be easily tilted from the upright state by slightly pushing the sleeve 61 in the axial direction by the moving means 52.

That is, the compressor can be in a so-called inoperative state even if the drive shaft 11 is rotated by reversing the complete destroke. On the other hand, at the time of starting, the moving means 52 forces the socket plate 1 to operate.
It is possible to tilt 6 Therefore, unlike the conventional case, it is possible to prevent the refrigerant from constantly circulating in the cooling cycle at a predetermined minimum discharge amount and forced to useless work even when it is not necessary.

Therefore, an unnecessary load is not applied to the engine, and as a result, the fuel efficiency of the automobile can be reduced. Furthermore, it is possible to avoid the risk of evaporator freezing.

Further, without using the clutch 2a as in the prior art, as described above, the variable displacement swash plate compressor 51 can be brought into a so-called inoperative state in which the variable displacement swash plate compressor 51 is not discharged. At 51, there is no need to use a heavy clutch 2a, and its construction is extremely simple. For this reason, workability in assembling the variable capacity compressor 51 is improved, which is advantageous in terms of cost and can be significantly reduced in weight. Further, the fuel efficiency of the automobile can be further improved. Then, conventionally, the load on the engine changes when the clutch is turned on and off, but the impact at this time also disappears and the riding comfort is improved.

The moving means 52 includes a push pin 62 that is movable in the axial direction and is in contact with the axial end surface of the sleeve, and a hydraulic mechanism section that moves by applying hydraulic pressure to the push pin 62. 63, it is possible to obtain a sufficient pressing force with a compact configuration.

It should be noted that the embodiments described above are described for facilitating the understanding of the present invention, and not for limiting the present invention. Therefore, each element disclosed in the above embodiments is intended to include all design changes and equivalents within the technical scope of the present invention.

For example, in the above-mentioned embodiment, the push pin 62 is configured to move in the direction of the sleeve 61 by applying hydraulic pressure by the hydraulic mechanism portion 63, but the present invention is not limited to this. Other drive means, such as a motor or pneumatics, can be used. Further, in the variable displacement compressor 51 of the above-described embodiment, the socket plate 16 is non-rotating, but it is also applicable to a rotating type variable displacement compressor.

[0054]

As described above, according to the present invention, a sleeve which is slidably fitted on a drive shaft in an axial direction and in which a socket plate is swingably engaged around a predetermined point is provided. Since the moving means for forcibly moving in the axial direction from the position where the inclination of the socket plate is perpendicular to the drive shaft to the position where it is tilted by a predetermined angle is provided, it is possible to slightly push the sleeve in the axial direction by this moving means. , The socket plate can be easily tilted from the upright state.

That is, by making a complete destroke reflexively, it is possible to make a so-called inoperative state in which the compressor is not discharged even if the drive shaft is rotated, while at the time of starting, the socket plate is forcibly forced by the moving means. Can be tilted. Therefore, unlike the conventional case, it is possible to prevent the refrigerant from constantly circulating in the cooling cycle at a predetermined minimum discharge amount and forced to useless work even when it is not necessary. Therefore, it is possible to reduce fuel consumption without applying an extra load to the engine. Furthermore, it is possible to avoid the risk of evaporator freezing.

Further, since the so-called inoperative state can be achieved without using a conventional clutch, the clutch can be eliminated, and the construction thereof becomes extremely simple. For this reason, workability in assembling this compressor is improved, which is advantageous in terms of cost and can be significantly reduced in weight. Further, the fuel efficiency of the automobile can be further improved. And the clutch on
The shock at the time of off can be eliminated and the riding comfort will be improved.

Further, since the moving means has a rod that is movable in the axial direction and is brought into contact with the axial end surface of the sleeve, and a hydraulic mechanism portion that applies hydraulic pressure to the rod to move the rod. A sufficient pressing force can be obtained with a compact structure.

[Brief description of drawings]

FIG. 1 is a schematic sectional view showing a piston discharge process in a variable displacement swash plate compressor according to an embodiment of the present invention.

FIG. 2 is a perspective view showing the push pin shown in FIG.

FIG. 3 is a cross-sectional view taken along the line AA shown in FIG.

FIG. 4A is a diagram schematically showing a complete destroke state in which the socket plate is upright, and FIG. 4B is a diagram schematically showing a state in which the sleeve is moved by the push pin and the socket plate is inclined. FIG.

FIG. 5 is a schematic cross-sectional view showing a piston discharge process in a conventional variable displacement swash plate compressor.

[Explanation of symbols]

 11 ... Drive shaft, 12 ... Crank chamber, 16 ... Socket plate, 23 ... Piston, 25 ... Cylinder, 29 ... Suction port, 52 ... Moving means, 61 ... Sleeve, 62 ... Push pin (rod), 63 ... Hydraulic mechanism part , 64 ... connecting pin, Cv ... control valve,

Claims (2)

[Claims] 1. A socket plate (16), which is connected to a drive shaft (11) in a variable inclination angle and reciprocates in the axial direction by the rotation of the drive shaft (11), and this socket plate (16). This piston (23) and the piston (23) connected to
Has a cylinder (25) that slides inside the crank chamber (12), and the piston (23) is responsive to the pressure of the refrigerant returning to the suction port (29) of the cylinder (25). In a variable displacement compressor provided with a control valve (Cv) for controlling the tilt angle by adjusting the pressure in the crank chamber (12) acting on the back surface, an axial slide is provided on the drive shaft (11). A sleeve (61) movably fitted and engaged with the socket plate (16) swingably around a predetermined point is provided with an inclination of the socket plate (16) with respect to the drive shaft (11). A variable capacity swash plate compressor characterized in that a displacement means (52) for forcibly moving in the axial direction from a position at a right angle to a position inclined by a predetermined angle is provided. 2. The moving means (52) includes the sleeve (61).
A rod (62) that is movable in the axial direction and is brought into contact with the axial end surface of the rod, and a hydraulic mechanism section (63) that applies hydraulic pressure to the rod (62) to move the rod (62). The variable capacity swash plate compressor according to claim 1.