JP2001263224A - Piston type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a piston type compressor eliminating a driving shaft energizing spring and capable of easily assembling a structure for regulating a slide movement of a driving shaft. SOLUTION: In a housing hole 12a penetratingly formed in a cylinder block 12, an abutting member 60 is pressed in and fixed to a rear end part of the driving shaft 16. The driving shaft 16 regulates the slide movement of the driving shaft 16 in the direction for approaching a valve-port forming body 14 by abutment of the valve-port forming body 14 and the abutting member 60 for blocking up the opposite side of the inserting side of the driving shaft 16 of the housing hole 12a. This piston type compressor is set so as to form prescribed clearance between a second movement regulating part 14e of the valve- port forming body 14 and the abutting member 60 in a state of regulating the slide movement in the direction for going away from the valve-port forming body 14 of the driving shaft 16 in abutment by a first movement regulating part 11a.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a piston type compressor used for a vehicle air conditioner, for example.

[0002]

2. Description of the Related Art As this type of compressor, for example,
There is a variable displacement type swash plate type compressor (hereinafter simply referred to as a compressor) as disclosed in Japanese Patent Application Publication No. 000-2180.

This compressor has a drive shaft to which a rotational driving force from an engine is transmitted, a cam plate (swash plate) operatively connected to the drive shaft so as to be rotatable and tiltable, A piston coupled to the cylinder bore and reciprocally accommodated in the cylinder bore. In this configuration, the rotational motion of the engine is converted into a reciprocating motion of the piston via the drive shaft and the cam plate. Further, in this compressor, in order to change the stroke of the piston, the inclination of the cam plate can be changed by changing the pressure of the crank chamber in which the cam plate is housed.

Further, in this compressor, in order to restrict the sliding movement of the drive shaft in the axial direction within the housing, the drive shaft is constantly moved in the axial direction by using a coil spring (drive shaft biasing spring). Pressing is performed. The slide movement of the drive shaft is restricted in order to prevent a collision between the head of the piston and the valve forming body (valve / port forming body) due to the sliding movement of the drive shaft.

However, in order to reliably prevent the above-described sliding movement of the drive shaft in the axial direction, it is necessary to use a coil spring having a large spring force. Accordingly, the durability of a portion (such as a thrust bearing) that receives a large load from the coil spring is reduced,
A problem such as an increase in power loss of the compressor in this portion occurs. The increase in power loss in the compressor has a considerable adverse effect on the fuel consumption of the vehicle (engine).

As a configuration for solving this problem, for example, there is a configuration of a variable displacement type swash plate compressor disclosed in Japanese Utility Model Publication No. 2-23827. In this configuration, the above-described coil spring (drive shaft biasing spring) is deleted, and instead, a slide movement restricting member (adjustment screw) that can abut on the shaft end of the drive shaft is provided at the end of the drive shaft. The inner hole of the housing is provided with a threaded process to regulate the sliding movement of the drive shaft.

[0007]

However, in the configuration disclosed in Japanese Utility Model Publication No. 2-23827, in order to realize a smooth rotation operation of the drive shaft, the slide movement restricting member and the drive shaft are not moved. It is necessary to keep the gap with the shaft end properly. For this purpose, when assembling the slide movement restricting member to the housing inner hole, from the outside of the housing with the housing inner hole being exposed,
It is necessary to manage the gap between the shaft end existing inside the slide movement regulating member and the regulating member. In other words, if the thickness of the regulating member is not strictly controlled, the gap cannot be secured properly, etc., which causes an increase in component cost and makes assembly and adjustment difficult. In addition, the threading of the inner hole of the housing has a large screw diameter and is directly processed in the housing, so that handling during the processing becomes difficult.

SUMMARY OF THE INVENTION An object of the present invention is to provide a piston type compressor which can eliminate a drive shaft biasing spring and can simplify a structure for regulating a slide movement of a drive shaft. is there.

[0009]

According to a first aspect of the present invention, a crankshaft is formed in a housing and a drive shaft is rotatable so as to pass through the crankcase. A cylinder bore is formed in a cylinder block constituting a part of the housing, a cam plate is connected to the drive shaft in the crank chamber so as to be integrally rotatable, and a single-headed piston is connected to the cam plate in the cylinder bore. Are reciprocally accommodated,
In a piston type compressor, a housing is provided with a valve / port forming body having a suction port corresponding to a cylinder bore, a suction valve, a discharge port, and a discharge valve so as to close the cylinder bore. A first movement restricting portion and a second movement restricting portion for restricting the sliding movement in the axial direction of the drive shaft are provided, and the first movement restricting portion controls the sliding movement of the drive shaft in a direction away from the valve / port forming body. The second movement restricting portion receives the contact member provided on the drive shaft and restricts the slide movement of the drive shaft in the direction close to the valve / port formation body while restricting the contact. An accommodation hole for accommodating an end portion of the drive shaft is formed through the cylinder block, and the valve / port forming body is joined to the cylinder block on a side opposite to an insertion side of the drive shaft. A state in which the accommodation hole is closed and the valve / port forming body facing the accommodation hole is used as the second movement restricting portion, and the sliding movement of the drive shaft is restricted by the first movement restricting portion. In the above, the gist is that a predetermined gap is provided between the second movement restricting portion and the contact member.

According to the present invention, the sliding movement of the drive shaft in the axial direction is restricted by the contact between the contact member and the second movement restricting portion. Accordingly, various problems associated with the slide movement can be solved without the drive shaft urging spring in the related art. Therefore, it is possible to solve the problems that occur when the drive shaft biasing spring is provided, such as a decrease in durability of a portion that receives the load and an increase in power loss of the compressor in this portion.

Further, since the valve / port forming body is used as the second movement restricting portion, the structure for restricting the movement of the drive shaft can be simplified. Further, the second movement in a state in which the slide movement of the drive shaft is restricted by the first movement restricting portion.
The gap between the movement restricting portion and the contact member can be set by changing the position where the contact member is attached to the drive shaft, and the actual alignment is easy.

[0012] Further, the space for accommodating the end portion of the drive shaft (the inner space of the accommodation hole) is used to construct a structure for restricting the movement of the drive shaft. It is possible to prevent the machine from becoming large.

According to a second aspect of the present invention, in the first aspect, the contact member is fixed to an outer peripheral side of a drive shaft. According to the present invention, for example, as compared with a case where the contact member is inserted and fixed into a hole or the like formed at the shaft end of the drive shaft, it is easier to secure the assembling strength of the contact member to the drive shaft. Is difficult to shift. In a case where the contact member needs to be formed in a hollow shape or the like, it is easy to secure the thickness of the contact member.

According to a third aspect of the present invention, in the first or the second aspect of the present invention, the valve / port forming body includes a port forming plate in which the suction port and the discharge port are formed, and the suction valve. And a sliding movement of the drive shaft in a direction in which the drive shaft approaches the valve / port formation body is regulated by the contact member abutting on the valve plate. Is the gist.

According to the present invention, since the valve plate is formed using a material having better wear resistance than the port forming plate, the wear resistance of the second movement restricting portion is improved. Therefore, it is possible to prevent wear and deterioration of the second movement restricting portion due to sliding with the contact member.

According to a fourth aspect of the present invention, in the first aspect, the contact member is press-fitted and fixed to a drive shaft. According to the present invention, a metal member such as a bolt or an adhesive is not required for fixing the contact member to the drive shaft, and the assembling is a simple operation of merely pressing down via a press-in jig. Further, the contact member can be positioned by a simple operation of adjusting the degree of press-fitting of the contact member to the drive shaft.

According to a fifth aspect of the present invention, in the fourth aspect, the contact member is made of a material having a coefficient of thermal expansion equivalent to that of the material of the drive shaft. According to the present invention, the difference in the amount of thermal expansion between the drive shaft and the contact member hardly occurs, and the interference of the contact member or the drive shaft hardly changes. As a result, cracks may occur in the contact member and the drive shaft due to the increase in the interference, and the contact member may be displaced with respect to the drive shaft due to the decrease in the interference, and the contact member and the second moving member may be moved. It is possible to prevent the maximum clearance with the restricting portion from changing.

According to a sixth aspect of the present invention, in the first aspect of the present invention, a first screw portion is formed on the contact member, and a second screw portion is formed on the drive shaft. The gist is that it is fixed to the screw portion.

According to the present invention, the mounting position of the contact member on the drive shaft can be adjusted by changing the screwing amount of the contact member into the drive shaft.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, first and second embodiments in which the present invention is embodied in a piston type variable displacement swash plate type compressor used in a vehicle air conditioner will be described.

(First Embodiment) As shown in FIG. 1, a front housing 11 is joined to a front end of a cylinder block 12. The cylinder block 12 is made of an aluminum-based metal material. Rear housing 1
3 is joined to the rear end of the cylinder block 12 via a valve / port forming body 14. Front housing 1
1, the cylinder block 12 and the rear housing 13
It is fastened and fixed by through bolts and the like, and forms a housing of the compressor. In addition, let the left of FIG. 1 be the front of a compressor, and let the right be the back.

The valve / port forming body 14 is provided with the port forming plate 1.
A suction valve forming plate (valve plate for forming a suction valve) 14b made of a quenched carbon steel strip is provided in front of 4a, a discharge valve forming plate 14c is provided on the rear side, and a discharge valve forming plate 14c is provided on the rear side of the discharge valve forming plate 14c. Each of the retainer forming plates 14d is superposed. The valve / port forming body 14 is joined to the rear end face 12b of the cylinder block 12 with the front face of the suction valve forming plate 14b.

The crank chamber 15 includes the front housing 1
1 and the cylinder block 12 are defined. The drive shaft 16 is disposed so as to pass through the crank chamber 15, and is rotatably supported between the front housing 11 and the cylinder block 12. Drive shaft 1
Reference numeral 6 is made of an iron-based metal material. Drive shaft 16
Is supported by the front housing 11 via a radial bearing 17. The accommodation hole 12a is provided through the center of the cylinder block 12. Drive shaft 1
The rear end 6 is inserted into the accommodation hole 12a, and is supported via a radial bearing 18 as a bearing for rotatably supporting the drive shaft.

The front end of the drive shaft 16 projects through the front wall of the front housing 11 to the outside. The electromagnetic clutch 23 as a power transmission mechanism is interposed between the engine Eg of the vehicle as an external drive source and the drive shaft 16. The rotor 24 of the electromagnetic clutch 23 is rotatably supported on the outer wall surface of the front housing 11 via an angular bearing 25. A belt 26 from the engine Eg is wound around the outer periphery of the rotor 24. A hub 27 also serving as an elastic member is fixed to the front end of the drive shaft 16 and elastically supports the armature 28 on the outer peripheral side.

The armature 28 includes a front housing 1
On the side opposite to 1, it is arranged facing the rotor 24. The electromagnetic coil 29 is supported on the outer wall surface of the front housing 11 and is arranged in the rotor 24.

When the electromagnetic coil 29 is energized by energization while the engine Eg is running, the armature 2
Electromagnetic attraction is applied between the rotor 8 and the rotor 24. Accordingly, the armature 28 moves rearward on the axis L against the elastic force of the hub 27 and presses against the rotor 24, so that the electromagnetic clutch 23 is turned on. In this ON state, the engine E
The driving force of g is transmitted to the driving shaft 16 via the belt 26 and the electromagnetic clutch 23 (FIG. 1). When the electromagnetic coil 29 is demagnetized from this state, the armature 28
The electromagnetic clutch 23 is turned off by being separated from the rotor 24 toward the front side of the axis L by the elastic force of. In this off state, transmission of the driving force from the engine Eg to the drive shaft 16 is shut off (FIG. 2).

The rotary support 30 is fixed to the drive shaft 16 in the crank chamber 15. Thrust bearing 2
0 is interposed between the rotary support 30 and the inner wall surface 11a of the front housing 11. The swash plate 31 as a cam plate can be tilted to the drive shaft 16 and
Are supported so as to be slidable in the direction of the axis L.

The hinge mechanism 32 includes the rotating support 30 and the swash plate 3.
1 is interposed. The swash plate 31 is used for the rotation support 3.
0 through the hinge mechanism 32 via the hinge mechanism 32,
It can rotate integrally with the drive shaft 16 and can change the angle of inclination with respect to the axis L (the angle between a plane perpendicular to the axis L).

The minimum tilt angle defining section 34 is provided between the swash plate 31 and the cylinder block 12 on the drive shaft 16. The minimum inclination angle defining portion 34 is formed by fitting a ring-shaped member to the outer peripheral surface of the drive shaft 16. As shown by the two-dot chain line in FIG. 1, the minimum inclination angle of the swash plate 31 is defined by contact with the minimum inclination angle defining part 34. As shown by the solid line in FIG. 1, the maximum inclination angle of the swash plate 31 is defined by contact with the rotating support 30.

A plurality of (only one is shown in the drawing) cylinder bores 33 are formed in the cylinder block 12 so as to penetrate the accommodation hole 12a in the direction of the axis L. The single-headed piston 35 is accommodated in each cylinder bore 33 so as to be able to reciprocate. The piston 35 shown in the drawing is located at the top dead center. A space for compressing the refrigerant gas is defined in the cylinder bore 33 by closing the front and rear sides of the front end surface of the piston 35 and the front surface of the valve / port forming body 14 (the suction valve forming plate 14b). . Piston 35
Are moored to the outer peripheral portion of the swash plate 31 via the shoes 36. Then, the rotational movement of the drive shaft 16 is
The swash plate 31 is transmitted to the swash plate 31 via the hinge mechanism 32, and only the forward and backward swings are taken out from the rotational movement of the swash plate 31 via the shoe 36 and transmitted to the piston 35. The piston 35 reciprocates in the cylinder bore 33. Is done.

A suction chamber 37 serving as a suction pressure area is defined in the center of the rear housing 13. The discharge chamber 38 as a discharge pressure region is defined in the rear housing 13 on the outer peripheral side of the suction chamber 37. The suction chamber 37 and the discharge chamber 38 are respectively provided with the valve / port forming body 14.
Are adjacent to each cylinder bore 33. The suction port 39 and the discharge port 40 are connected to the valve / port forming body 14.
Are formed corresponding to the respective cylinder bores 33. The suction valve 41 is formed on the suction valve forming plate 14b so as to correspond to the suction port 39. The discharge valve 42 is formed corresponding to the discharge port 40 on the discharge valve forming plate 14c. The retainer 43 is
It is formed corresponding to the discharge valve 42 on the retainer forming plate 14d. The retainer 43 is for defining the maximum opening of the discharge valve 42.

Then, the refrigerant gas in the suction chamber 37 moves from the top dead center position of the piston 35 to the bottom dead center side, so that the cylinder gas flows through the suction port 39 and the suction valve 41.
(Compression chamber). The refrigerant gas sucked into the cylinder bore 33 is compressed to a predetermined pressure by moving from the bottom dead center position of the piston 35 to the top dead center side, and then is discharged to the discharge chamber 38 through the discharge port 40 and the discharge valve 42. Discharged.

The compressive load of the refrigerant gas acting on the piston 35 is received by the inner wall surface 11a of the front housing 11 via the shoe 36, the swash plate 31, the hinge mechanism 32, the rotary support 30 and the thrust bearing 20.
In other words, the sliding movement of the integrated body such as the drive shaft 16, the swash plate 31, the rotary support 30 and the piston 35 toward the front of the axis L by the action of the compressive load is performed via the rotary support 30 and the thrust bearing 20. , Front housing 1
The contact is restricted by the inner wall surface 11a. Therefore, in the present embodiment, the inner wall surface of the front housing 11 forms the first movement restricting portion 11a.

The air supply passage 44 is provided between the discharge chamber 38 and the crank chamber 1.
5 is communicated. The capacity control valve 46 is disposed on the air supply passage 44. The capacity control valve 46 includes a valve body 46a that opens and closes the air supply passage 44, an electric drive unit 46b that operates the valve body 46a by external electric control, and a valve body 46a that increases the opening degree. Open spring 46c to urge
And an electromagnetic type having the following. As a characteristic of the capacity control valve 46, when the amount of electric power supplied to the electric drive unit 46b increases, the valve body 46a operates to reduce the opening degree of the air supply passage 44 against the opening spring 46c.
Conversely, when the amount of power supplied to the electric drive unit 46b decreases,
The valve body 46a is operated by the opening spring 46c so as to increase the opening degree of the air supply passage 44.
When the power supply to 6b is stopped, the valve body 46a fully opens the air supply passage 44 by the opening spring 46c.

The accommodation hole 12a is closed at the rear end side by the valve / port forming body 14. The accommodation hole 12a and the suction chamber 37 communicate with each other through a passage 50 formed in the valve / port formation body 14. The passage 50 is formed at a position substantially facing the center of the drive shaft 16.

The drive shaft 16 is provided with a communication hole 51 for communicating the rear side of the housing hole 12a with the crank chamber 15. In the communication hole 51, the entrance 51a is the radial bearing 1
The outlet 51 b is formed so as to open to the rear end face of the drive shaft 16 at a position rearward of the drive shaft 7. Communication hole 51, accommodation hole 12
a and the passage 50 constitute a bleed passage that connects the crank chamber 15 and the suction chamber 37, and the passage 50 is formed to have a size that functions as a throttle.

In the compressor of the present embodiment, the capacity control valve 46
By adjusting the opening degree of the air supply passage 44, the introduction amount of the high-pressure discharge refrigerant gas into the crank chamber 15 is adjusted,
The pressure in the crank chamber 15 is changed from the relationship with the amount of refrigerant gas released to the suction chamber 37 through the bleed passage.
Therefore, the difference between the pressure in the crank chamber 15 and the pressure in the cylinder bore 33 via the piston 35 is changed, and the inclination angle of the swash plate 31 is changed. As a result, the stroke amount of the piston 35 is changed, and the discharge capacity is adjusted.

For example, when the pressure in the crank chamber 15 increases and the difference between the pressure in the cylinder bore 33 and the pressure through the piston 35 increases, the inclination angle of the swash plate 31 decreases, and the displacement of the compressor decreases. Conversely, when the pressure in the crank chamber 15 decreases and the difference from the pressure in the cylinder bore 33 decreases,
As the inclination angle of the swash plate 31 increases, the displacement of the compressor increases.

In the compressor having the above structure, when the electromagnetic clutch 23 is turned off, the power supply to the displacement control valve 46 is stopped almost simultaneously, and the displacement control valve 46 is connected to the supply passage 4.
4 will be fully opened. Therefore, the compressor immediately minimizes the inclination angle of the swash plate 31 after the electromagnetic clutch 23 is turned off, and even if the next electromagnetic clutch 23 is turned on shortly after being turned off, the compressor is started at the maximum load torque. The state is changed from the small minimum discharge capacity state. Therefore, a shock generated at the time of starting the compressor is reduced.

When the vehicle attempts to shift to a rapid acceleration state (for example, when the accelerator pedal is depressed greatly), the power supply to the displacement control valve 46 is stopped regardless of the cooling load, and the compressor discharges the minimum discharge displacement. State (accelerated cut). Therefore, the compressor driving load of the engine Eg is reduced, and a sharp acceleration state of the vehicle can be obtained.

The acceleration cut can also be achieved by turning off the electromagnetic clutch 23. However, when the acceleration cut is performed by controlling the electromagnetic clutch 23,
With the on / off shock of the electromagnetic clutch 23,
This causes a problem that the drivability of the vehicle deteriorates. Therefore, as described above, achieving the acceleration cut in the minimum displacement state of the compressor has an advantage that the problem of deterioration in drivability of the vehicle can be solved.

Next, a characteristic configuration of the present embodiment will be described. As shown in FIGS. 1 and 2, the contact member 60 has a cylindrical shape, and is fitted into a small-diameter portion 16 b formed at the rear end of the drive shaft 16. The outer diameter of the contact member 60 is
It is set smaller than the inner diameter of the radial bearing 18 when assembled to the small diameter portion 16b. The rear end surface of the contact member 60 forms a contact portion 60a.
Valve / port forming body 14 facing the inside of the receiving hole 12a
The front surface of the (suction valve forming plate 14b) is the second movement restricting portion 14e.
Has made. The contact member 60 has a thermal expansion coefficient equal to that of the material of the drive shaft 16 (iron-based metal material) and a material constituting the cylinder block 12 (aluminum-based metal material).
Are made of a different material (for example, an iron-based metal material), and the surface layer is hardened by quenching or the like.

Then, as shown in FIG.
Is adjusted so that the following relationship is established. In a state where the slide movement of the drive shaft 16 is restricted by the contact between the rotation support 30 and the first movement restricting portion 11a, the second movement of the contact portion 60a on the drive shaft 16 side and the valve / port forming body 14 is performed. Regulator 14e
Is formed between the front end surface of the piston 35 at the top dead center position and the front surface of the valve / port forming body 14 (suction valve forming plate 14b) opposed thereto. And the clearance X3 formed between the rotor 24 of the electromagnetic clutch 23 and the armature 28 in the off state. Note that, for example, the clearance X1 is about 0.1 mm, the clearance X2 is about 0.3 mm, and the clearance X3 is about 0.5 mm, and the respective clearances X1 to X3 are exaggerated in the drawings.

Next, a method of assembling the compressor having the above-described structure, in particular, a procedure for press-fitting the contact member 60 into the small-diameter portion 16b of the drive shaft 16 using the press-fitting jig 63 will be described. FIG.
3 shows an enlarged view of a main part of the compressor before the electromagnetic clutch 23, the rear housing 13 and the valve / port forming body 14 are assembled. That is, FIG. 3 is in a state similar to FIG. 2 except that the electromagnetic clutch 23, the rear housing 13, and the valve / port forming body 14 are not assembled. In this state, the housing hole 12a is opened outward on the side (rear side) opposite to the side where the drive shaft 16 is inserted. The contact member 60 is pressed into the small diameter portion 16b from the open side.

FIGS. 3A and 3B show a press-fitting jig 63 used for press-fitting the contact member 60 into the drive shaft 16. This press-fitting jig 63 is
The front end face has a columnar shape larger than 2a, and a clearance management section 63a and a clearance management section 63a
Pressing portion 6 smaller in diameter than accommodation hole 12a protruding on the inner peripheral side of
3b. The pressing portion 63b is connected to the contact portion 60.
The protrusion protrudes from the clearance management unit 63a by the maximum amount of clearance X1 set between the second movement restriction unit 14e and the second movement restriction unit 14e.

Then, as shown in FIG. 3B, the clearance management portion 63a of the press fitting jig 63 is pressed until the clearance end of the cylinder block 12 comes into contact with the rear end face 12b of the cylinder block 12 around the opening of the accommodation hole 12a. Abutment portion 60a via portion 63b
, The contact member 60 is pushed against the drive shaft 16. Therefore, the sliding movement of the drive shaft 16 is the first movement.
The state where the contact is restricted by the movement restricting portion 11a is brought about, and the clearance managing portion 63 of the pressing portion 63b is provided.
a predetermined clearance X between the contact portion 60a and a virtual plane including the rear end surface 12b of the cylinder block 12 (the surface on which the second movement restricting portion 14e is disposed).
1 will be set.

Next, the characteristic operation of the present embodiment will be described. For example, when the electromagnetic clutch 23 is turned off and the acceleration cut is performed from the maximum discharge capacity state of the compressor as described above, the capacity control valve 46 is set in the supply passage 44 in the fully closed state.
Will suddenly fully open. Therefore, the high-pressure discharge refrigerant gas in the discharge chamber 38 is rapidly supplied to the crank chamber 15,
Since the bleed passage does not allow the rapid inflow of the refrigerant gas to escape, the pressure in the crank chamber 15 rises sharply.
When the pressure in the crank chamber 15 rises sharply, the pressure in the crank chamber 15 rises excessively, or the momentum at which the swash plate 31 reduces the inclination angle becomes excessive. as a result,
A swash plate 31 (shown by a two-dot chain line in FIG. 1) having a minimum inclination angle is pressed against the minimum inclination angle defining portion 34 with excessive force, or the rotating support 30 is strongly pushed rearward via the hinge mechanism 32. Will pull. Therefore, the drive shaft 1
6 receives the strong moving force toward the rear side of the axis L and slides.

However, the drive shaft 16 is connected to the first movement restricting portion 11 via the rotary support 30 and the thrust bearing 20.
The sliding movement toward the rear side of the axis L is started from the state where the movement is restricted by a, and even if the movement is restricted by the contact between the contact part 60a and the second movement restriction part 14e, during this time, The clearance between the piston 35 at the top dead center position and the valve / port forming body 14 (the maximum amount X2), which has more travel than the movement amount, that is, the clearance X1;
Also, the clearance (maximum amount X3) between the rotor 24 and the armature 28 of the electromagnetic clutch 23 in the off state does not disappear. Therefore, during operation of the compressor, it is possible to prevent the piston 35 from colliding with the valve / port forming body 14 when located at the top dead center. Can be prevented from being damaged. In addition, even when the electromagnetic clutch 23 is in the off state, generation of abnormal noise and vibration and heat generation due to sliding between the rotor 24 and the armature 28 can be prevented, and unnecessary power transmission can be prevented.

The present embodiment having the above configuration has the following effects. (1) The contact between the contact portion 60a and the second movement restricting portion 14e restricts the sliding movement of the drive shaft 16 to the rear of the axis L. Accordingly, various problems associated with the slide movement can be solved without the drive shaft urging spring in the related art. Therefore, problems such as a decrease in the durability of the thrust bearing 20 that receives the load and an increase in the power loss of the compressor in the thrust bearing 20, which occur when the drive shaft biasing spring is provided, are solved. can do. Reduction of the power loss of the compressor has a favorable effect on the fuel consumption of the vehicle (engine Eg). In addition, the fact that the drive shaft biasing spring can be eliminated requires a configuration accompanying the drive shaft bias spring, for example, the drive shaft 1.
Bearings and the like for interrupting power transmission with the motor 6 can be omitted, and the configuration can be simplified.

(2) As the second movement restricting portion 14e, a valve
The port forming body 14 (suction valve forming plate 14b) is used, and the structure for restricting the movement of the drive shaft 16 is simplified. (3) For example, when a contact portion is formed directly on the drive shaft 16 (for example, the shaft end is used as the contact portion), finish grinding or the like of the drive shaft 16 (the contact portion) is performed by actual matching. , The relationship between the clearance X1 and the clearances X2 and X3 (X1
<X2, X3) is set, and the operation becomes troublesome. However, in the present embodiment, the contact portion is provided by a contact member 60 which is a separate member from the drive shaft 16. Therefore, the clearance X1, the clearance X2,
The relation setting of X3 can be achieved by changing the position of the contact member 60 with respect to the drive shaft 16, and the actual alignment is easy.

(4) By using the space for accommodating the rear end of the drive shaft 16 (the inner space of the accommodation hole 12a), a structure for restricting the movement of the drive shaft 16 is provided. The compressor can be prevented from becoming large.

(5) The contact member 60 is fixed to the outer peripheral side of the drive shaft 16. According to this, for example, the drive shaft 1
As compared with the case where the contact member is inserted and fixed in a hole or the like (for example, the outlet 51b) formed at the shaft end of No. 6, the assembling strength of the contact member 60 to the drive shaft 16 is easily ensured, and the contact member 60 Is difficult to shift. When the contact member 60 needs to be formed in a hollow shape or the like, the thickness of the contact member 60 can be easily secured.

(6) The contact member 60 is moved to the suction valve forming plate 14b.
, The sliding movement of the drive shaft 16 toward the rear side of the axis L is restricted. Suction valve forming plate 14
b is made of a material having higher abrasion resistance than the port forming plate 14a.
e has improved wear resistance. Therefore, the second movement restricting portion 14e (sliding with the contact portion 60a) (the valve / port forming body 1).
4) It is possible to prevent the deterioration of wear and, consequently, the increase in the clearance X1, and to prevent the collision between the piston 35 and the valve / port formation 14 and the sliding between the rotor 24 and the armature 28 for a long period of time. Can play.

(7) The surface layer of the contact member 60 is hardened by quenching or the like, and the suction valve forming plate 14b is formed using a hard quenched carbon steel strip. Therefore, for example, as compared with a case where the contact member 60 is brought into contact with the second movement restricting portion provided by the iron material whose surface is not hardened, the contact member 60 on the side of the second movement restricting portion is used. It becomes possible to improve wear resistance.

(8) The contact member 60 is press-fitted and fixed to the small diameter portion 16b of the drive shaft 16. Therefore, fixing of the contact member 60 to the drive shaft 16 does not require metal fittings such as bolts or an adhesive, and the assembling is a simple operation of merely pressing down via the press-in jig 63. Further, the positioning of the contact portion 60a is a simple operation only by adjusting the degree of press-fitting of the contact member 60 to the drive shaft 16.

(9) The contact member 60 is made of a material (iron-based metal material) having the same thermal expansion coefficient as the material of the drive shaft 16 (iron-based metal material) into which it is pressed. Therefore, there is almost no difference in the amount of thermal expansion between the drive shaft 16 and the contact member 60, and the interference of the drive shaft 16 hardly changes. As a result, a crack may occur in the contact member 60 or the drive shaft 16 due to an increase in the interference, or the contact member 60 (the contact portion 60a) due to a decrease in the interference.
Can be prevented from being displaced with respect to the drive shaft 16 to change the clearance X1.

(10) When press-fitting the contact member 60 to the drive shaft 16, the press-fitting jig 63 used for press-fitting pushes the contact member 60 against the drive shaft 16 in the accommodation hole 12a. As well as a clearance management section 63a for defining the amount of entry of the pressing section 63b into the accommodation hole 12a. Therefore, in the process of press-fitting the contact member 60 into the drive shaft 16, it is possible to create a state in which the slide movement of the drive shaft 16 is restricted by the first movement restricting portion 11 a at the same time, and the clearance of the pressing portion 63 b is further reduced. Management unit 63a
The clearance X1 can be set at the same time by a suitable protruding height.

(11) The outer diameter of the contact member 60 is set smaller than the inner diameter of the radial bearing 18. According to this, the drive shaft 16 is kept in a state where the contact member 60 is press-fitted.
Can be removed from the radial bearing 18. Therefore, maintenance work becomes easy.

(12) The electromagnetic capacity control valve 46 is responsive to, for example, a suction pressure, which is internal information of the compressor, and is compared with a pressure-sensitive valve which is internally autonomously operated so as to maintain the suction pressure at a predetermined value. In some cases, a sudden change of the displacement from the maximum discharge displacement to the minimum discharge displacement, that is, control such that the pressure in the crank chamber 15 rises sharply (response when the electromagnetic clutch 23 is turned off or acceleration cut). . Embodying the present invention in a compressor having such a capacity control valve 46 is particularly effective for achieving the effect.

(13) The capacity control valve 46 is connected to the air supply passage 44
Opening and closing the crank chamber 1 for the high-pressure discharge refrigerant gas
5 to adjust the discharge capacity of the compressor.
Therefore, for example, compared with a configuration in which only the bleed passage is opened and closed and the amount of refrigerant gas (lower pressure than the discharged refrigerant gas) flowing from the crank chamber 15 to the suction chamber 37 is adjusted to adjust the discharge capacity of the compressor. Thus, the pressure in the crank chamber 15 can be quickly increased. Therefore, when the acceleration cut or the electromagnetic clutch 23 is turned off, the discharge capacity can be quickly minimized. From another perspective, the capacity control valve 46
However, as compared with the case where only the bleed passage is opened and closed to adjust the discharge capacity, a problem that the pressure in the crank chamber 15 rises sharply easily occurs. Is particularly effective in achieving the effect.

(Second Embodiment) Hereinafter, according to FIG.
A second embodiment will be described. In the second embodiment, only differences from the first embodiment will be described, and the same members will be denoted by the same reference numerals and description thereof will be omitted.

As shown in FIG. 4, in this embodiment,
A contact member 53 whose outer diameter is larger than the inner diameter of the radial bearing 18 is press-fitted to the drive shaft 16, and the passage 50 is formed from the valve / port formation body 14 to the drive shaft 1.
6 differs from the first embodiment in that the communication hole 51 is omitted.

That is, the cylindrical contact member 53 is externally fitted and pressed into the small diameter portion 16b of the drive shaft 16, and the rear end face of the contact member 53 forms a contact portion 53a. Contact member 5
Reference numeral 3 denotes a material (for example, an iron-based metal material) having the same thermal expansion coefficient as the material of the drive shaft 16 (an iron-based metal material). As shown in the enlarged circle in FIG. 4, a coating made of a fluororesin such as polytetrafluoroethylene or a plated wear-resistant film 53b made of tin or the like is formed on the contacting portion 53a of the contacting member 53. ing.

In the present embodiment, a bleed passage (not shown) connecting the crank chamber 15 and the suction chamber 37 is formed so as to penetrate the cylinder block 12 and the valve / port forming body 14. The refrigerant gas in the crank chamber 15 can be introduced into the suction chamber 37.

Also in this embodiment, (1) to (6), (8) to (10) and (12),
In addition to the same effect as (13), the following effect is also obtained. (14) In the contact member 53, a wear-resistant coating 53b is formed on the contact portion 53a. Therefore, it is possible to prevent wear and deterioration of the contact portion 53a due to sliding with the second movement restricting portion 14e (the valve / port forming body 14), and further increase of the clearance X1.

(15) The outer diameter of the contact member 53 is set larger than the inner diameter of the radial bearing 18. According to this, the contact pressure of the contact portion between the contact member 53 and the valve / port forming body 14 can be reduced. Therefore, it is possible to suppress wear deterioration of the contact portion 53a and the second movement restricting portion 14e.

The present invention can be practiced in the following modes without departing from the spirit of the present invention. ○ The contact member is assembled to the drive shaft by screwing. For example, as shown in FIG. 5, a female screw portion 61b as a first screw portion is formed on the inner periphery of the contact member 61. A male screw portion 16e as a second screw portion that can be screwed with the female screw portion 61b is formed in the small diameter portion 16d of the drive shaft 16. The drive shaft 1 of the contact member 61 is provided between the two screw portions 16e and 61b.
An adhesive or the like is interposed in order to maintain a proper assembling position on the device 6. Accordingly, even when the contact member 61 rotating with the drive shaft 16 receives the rotational force due to the pressure contact with the second movement restricting portion 14e on the fixed side, the drive shaft 16
, And there is no possibility that the position of the contact portion 61a with respect to the drive shaft 16 shifts and the clearance X1 changes. According to this configuration, the contact member 61
By changing the screwing amount of the above, the mounting position of the contact member 61 on the drive shaft 16 can be adjusted.

As shown in FIG. 6, the second embodiment is modified so that the contact member 53 is press-fitted and fixed in the housing recess 16c formed on the rear end face of the drive shaft 16. According to this,
The size and the weight of the contact member 53 can be easily reduced.

In the first embodiment, the driving shaft 1
The diameter of the outlet 51b of the communication hole 51 is increased, and a cylindrical contact member is inserted and fixed in the outlet 51b. O The contact members 53 and 60 are not provided on the drive shaft 16, and the drive shaft 16 is directly contacted with the second movement restricting portion 14 e so as to restrict the slide movement of the drive shaft 16 in the axial direction. To be configured.

The contact members 53 and 60 are connected to the suction valve forming plate 1
A configuration is adopted in which the sliding movement in the axial direction of the drive shaft 16 is regulated by abutting the port forming plate 14a instead of the 4b.

The material of the contact members 53 and 60 is
The material of item No. 6 has a coefficient of thermal expansion that is not equivalent. In the first embodiment, a wear-resistant coating is formed on the contact portion 60a. In the first and second embodiments, the second movement restricting portion 14 of the valve / port forming body 14 is used.
Forming a wear-resistant coating on e.

As the abrasion resistance imparting treatment, besides forming the abrasion resistant film 53b as in the second embodiment, a nitrocarburizing treatment and metal spraying such as copper spraying may be mentioned. ○ A clutchless type power transmission mechanism between the engine and the engine Eg. In this case, the drive shaft 16 is always driven to rotate during the operation of the engine Eg.

The present invention is embodied in a wobble type variable displacement compressor. The present invention is embodied in a fixed displacement compressor in which the swash plate 31 is directly fixed to the drive shaft 16. Also in this fixed displacement compressor, for example, when the electromagnetic clutch 23 is in the off state, the drive shaft 16 may slide due to the inclination or vibration of the vehicle. That is, the cause of the sliding movement of the drive shaft 16 is not only the pressure fluctuation of the crank chamber 15. The present invention is also effective as a countermeasure.

Next, technical ideas other than the invention described in the claims that can be grasped from the embodiment will be described below. (1) When the slide movement of the drive shaft is restricted by the first movement restricting portion, the clearance formed between the contact member of the drive shaft and the second movement restricting portion is at the top dead center position. The piston type compressor according to claim 1, wherein the clearance is smaller than a clearance formed between the piston and the valve / port forming body.

(2) An electromagnetic clutch for operatively connecting an external drive source and a drive shaft is disposed outside the housing.
The electromagnetic clutch includes a rotor rotatably supported by a housing, an armature rotatably connected to a drive shaft via an elastic member, and an armature opposed to the rotor on the side opposite to the housing, and an armature having an elastic member. An electromagnetic coil that connects the two so that power can be transmitted by electromagnetically attracting the rotor side against the force, in a state where the slide movement of the drive shaft is restricted by the first movement restricting portion.
The clearance formed between the contact member of the drive shaft and the second movement restricting portion is smaller than the clearance formed between the rotor and the armature of the electromagnetic clutch in the off state. 2. The piston type compressor according to 1.

(3) The external dimension of the contact member is set smaller than the inner diameter of a bearing that rotatably supports the drive shaft.
The piston type compressor according to any one of (2).

(4) The abutting member is inserted and fixed in a hole or a hole formed in an end of the drive shaft, and is in any one of the technical ideas (1) and (2). Piston type compressor.

(5) Any one of the technical ideas (1) to (4), wherein at least one of the second movement restricting portion and the contact member is subjected to a wear resistance imparting treatment. A piston type compressor according to any one of the above.

(6) The piston type compression according to any one of claims 1 to 6 and technical ideas (1) to (5), wherein the second movement restricting portion and the contact member are made of different materials. Machine.

[0080]

As described above in detail, according to the first to sixth aspects of the present invention, in the piston type compressor, the drive shaft biasing spring is eliminated and the slide movement of the drive shaft is restricted. Can be easily assembled.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an outline of a variable displacement swash plate type compressor according to a first embodiment.

FIG. 2 is an enlarged sectional view of a main part of the compressor.

FIG. 3 is an enlarged view of a main part for explaining a procedure for assembling the compressor.

FIG. 4 is an enlarged sectional view of a main part showing a second embodiment.

FIG. 5 is an enlarged view of a main part showing another example.

FIG. 6 is an enlarged sectional view of a main part showing another example.

[Explanation of symbols]

11 front housing constituting the housing, 11
a: first movement restricting portion, 12: cylinder block forming a housing, 13: similarly rear housing, 12a ...
Housing hole, 14: valve / port forming body, 14b: suction valve forming plate as a valve plate for forming a suction valve, 14e: second
Movement restricting part, 15: crank chamber, 16: drive shaft, 16e
... a male screw part as a second screw part, 18 ... a radial bearing as a bearing for rotatably supporting the drive shaft,
23: electromagnetic clutch, 24: rotor, 27: hub as an elastic member, 28: armature, 29: electromagnetic coil, 3
1 ... swash plate as cam plate, 33 ... cylinder bore,
35: piston, 39: suction port, 40: discharge port, 41: suction valve, 42: discharge valve, 53, 60, 61 ...
Contact member, 61b: female screw portion as first screw portion, Eg
... Engine as an external drive source, X1 to X3 ... Clearance.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hiroaki Masukawa 2-1-1, Toyota-cho, Kariya-shi, Aichi Pref. Inside Toyota Industries Corporation (72) Inventor Satoshi Umemura 2-1-1, Toyota-cho, Kariya-shi, Aichi Pref. Inside Toyota Industries Corporation (72) Inventor Takeshi Takeshi 2-1-1 Toyota-cho, Kariya City, Aichi Prefecture Inside Toyota Industries Corporation (72) Inventor Hiroshi Kanayama 2-1-1 Toyota-machi, Kariya City, Aichi Prefecture Address Toyota Motor Corporation (72) Inventor Tetsuhiko Fukanuma 2-1-1 Toyotamachi, Kariya City, Aichi Prefecture Toyota Motor Corporation (72) Inventor Yuji Kubo 2-1-1 Toyotamachi, Kariya City, Aichi Prefecture Address Toyoda Automatic Loom Works F-term (reference) 3H076 AA06 BB32 BB40 BB41 CC16 CC28 CC31 CC36 CC84

Claims (6)

[Claims] A crank chamber is formed in a housing, and a drive shaft is rotatably supported so as to pass through the crank chamber. A cylinder block forming a part of the housing is formed with a cylinder bore, and a crank chamber is formed. , A cam plate is connected to the drive shaft so as to be integrally rotatable, a single-sided piston connected to the cam plate is reciprocally housed in the cylinder bore, and a suction port, a suction valve, and a discharge port corresponding to the cylinder bore are housed in the housing. In a piston type compressor in which a valve / port forming body having a port and a discharge valve is mounted so as to close a cylinder bore, a first member for restricting a sliding movement of a drive shaft in an axial direction with the housing is provided. A movement restriction part and a second movement restriction part are provided, and the first movement restriction part is separated from the valve / port forming body of the drive shaft. The second movement restricting portion receives the contact member provided on the drive shaft and abuts the slide movement in the direction approaching the valve / port formation body. A restricting structure, wherein a receiving hole for receiving an end portion of the drive shaft is formed through the cylinder block, and the valve / port forming body is inserted into the cylinder block on a side opposite to an insertion side of the drive shaft. The housing hole is closed by the joint arrangement, and the valve / port forming body facing the housing hole is used as the second movement restricting portion, and the slide movement of the drive shaft is restricted by the first movement restricting portion. A piston-type compressor which is set such that a predetermined gap is formed between the second movement restricting portion and the contact member in the closed state. 2. The piston type compressor according to claim 1, wherein the contact member is fixed to an outer peripheral side of a drive shaft. 3. The valve / port forming body includes a port forming plate on which the suction port and the discharge port are formed, and a valve plate for forming the suction valve, wherein the drive shaft is a valve / port. The piston type compressor according to claim 1 or 2, wherein sliding movement of the drive shaft in a direction approaching the formed body is regulated by the contact member abutting on the valve plate. 4. The piston type compressor according to claim 1, wherein said contact member is press-fitted and fixed to a drive shaft. 5. The piston type compressor according to claim 4, wherein said contact member is made of a material having a thermal expansion coefficient equivalent to that of a material of a drive shaft. 6. The piston type compression according to claim 1, wherein a first screw portion is formed on the contact member, and the first screw portion is fixed to a second screw portion formed on a drive shaft. Machine.