JPH08135568A - Reciprocation type compressor - Google Patents

Abstract

PURPOSE: To prevent seizure of a rotary valve even when lubrication oil around a rotary valve is in an insufficient state as core displacement inevitable to manufacture is allowed and to perform a smooth rotation of a drive shaft. CONSTITUTION: An intermediation member 50 having diameter larger than that of a drive shaft 6 is located between a rotary valve 40 and a drive shaft 6. A pin 42 is arranged at the front end of the rotary valve 40 and in a position situated eccentrically from an axis O as much as possible and a protrusion part 60 is arranged at the rear end of a driven shaft 6. The intermediate member 50 has an oblong hole 51 in which a protrusion 60 is fitted and movement in a radial direction of which is permitted and a round hole 52 which is extended through in the extension direction of the oblong hole 51 and in which the pin 42 is fitted and which allows peripheral movement of the intermediation member 50.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a reciprocating compressor suitable for air conditioning of vehicles.

[0002]

2. Description of the Related Art Conventionally, a reciprocating compressor described in JP-A-6-123280 has been known. In this compressor, a drive shaft is inserted and supported in a shaft hole of a cylinder block, and each piston is linked to a swash plate in a crank chamber cooperating with the drive shaft so as to be directly movable in each bore. . A housing is joined to the end surface of the cylinder block, an intake chamber for supplying the refrigerant gas into the bore is formed inside the housing, and the refrigerant gas compressed by the piston inside the bore is discharged outside the housing. Is formed. In addition, a radial communication path is communicated between each bore and the shaft hole, and a rotation path is provided at the rear end of the drive shaft, which has a suction path that sequentially communicates the communication path of each bore in the suction stroke with the suction chamber. The valves are coupled for synchronous rotation.

In this compressor, it is possible to compress the refrigerant gas by reciprocating each piston in each bore as the drive shaft rotates. At this time, in this compressor, since the rotary valve rotates in synchronization with the drive shaft, the refrigerant gas in the suction chamber is sequentially introduced into each bore through the suction passage of the rotary valve and the passage of each bore in the suction process. Inhaled. For this reason,
Since the suction action of the refrigerant gas continues smoothly and stably in each bore, the pressure loss is extremely small. In this way, this compressor can maintain sufficient volume efficiency regardless of whether it has a fixed capacity or a variable capacity.

[0004]

However, in the above-described compressor, the front end of the rotary valve is provided with the elongated hole having the opposing flat surface parallel to the shaft center, and the rear end of the drive shaft is provided with the convex portion. The rotary valve is coupled to the drive shaft by fitting the convex portion of the drive shaft into the elongated hole of the rotary valve. In a compressor that employs this coupling method, it has become clear that a force other than torque is transmitted from the drive shaft to the rotary valve. Therefore, in this compressor, if there is insufficient lubricating oil around the rotary valve, the rotary valve may cause seizure with the shaft hole, and a larger torque is required to drive the drive shaft, resulting in power loss. Will occur.

That is, as shown in FIGS. 14 to 18, opposed faces 81a, 81 parallel to the axis O at the front end of the rotary valve 80.
The elongated hole 81 having b is provided as a recess, and the convex portion 90 having the opposing flat surfaces 90a and 90b is provided at the rear end of the drive shaft (not shown) as a protrusion.
Consider a case where the convex portion 90 of the drive shaft is fitted in the long hole 81 of the rotary valve 80. Since the elongated hole 81 is guided by the convex portion 90 and is slidable in the radial direction, the opposing flat surfaces 81 a, 81
There is a gap between b and the opposing flat surfaces 90a and 90b. Therefore, the convex portion 90 is in point contact.

At this time, the rotation center O of the drive shaft, which is the shaft center,
14 and the rotation center Q of the rotary valve 80 have some misalignment e due to an unavoidable manufacturing error, the point A of the convex portion 90 is long in the state shown in FIG. 14 in which the rotation angle of the drive shaft is 0 °. The point B of the convex portion 90 is not in contact with the facing plane 81b of the elongated hole 81, but is in contact with the facing plane 81a of the hole 81. After that, the rotation angle of the drive shaft is θ (0 <θ <45) ° in FIG.
In the state shown in FIG. 6, the point A of the convex portion 90 abuts on the facing flat surface 81a of the long hole 81, and the point B of the convex portion 90 is long hole 81.
Abuts on the facing flat surface 81b. In the state shown in FIG. 16 in which the rotation angle of the drive shaft is 45 °, the point A of the convex portion 90 does not abut on the facing flat surface 81 a of the elongated hole 81, and the point B of the convex portion 90.
The point comes into contact with the facing flat surface 81b of the long hole 81. The same applies to the states shown in FIGS. 17 and 18 in which the rotation angles of the drive shaft are 90 ° and 135 °. When the rotation angle of the drive shaft reaches 180 °, points A and B alternate and the state shown in FIG. 14 is obtained.

Thus, in this compressor, the rotation of the drive shaft can be transmitted from the convex portion 90 to the rotary valve 80 via the elongated hole 81. Further, the rotation center O of the drive shaft and the rotation valve 80
Even if there is a center misalignment e with the rotation center Q of
Since is allowed to slide in the radial direction, the misalignment e can be absorbed. However, in the conventional coupling method, both the points A and B of the convex portion 90 come into contact with the opposing flat surfaces 81a and 81b of the elongated hole 81, so that the driving force of the drive shaft is applied to the rotary valve 80 at the points A and B. Acts only once per half rotation of the drive shaft, and during the other periods,
Only the point or the point B comes into contact with one of the facing planes 81a and 81b of the elongated hole 81, so that the driving force of the drive shaft only acts on the rotary valve 80 at the point A or the point B.

As described above, while the driving force is applied to the rotary valve 80 at only one point of the convex portion 90, the rotary valve 80 moves from the drive shaft.
If the rotation valve 80 is not pressed against the rotary valve 80 due to leaked gas pressure, the transmission of rotation to FIG.
See the following. First, M _r ; torque generated by tightening the rotary valve 80 in the shaft hole (torque generated by friction force) F _s ; driving force (vector) F ₀ ; reaction force of F _s (vector) μ; friction coefficient r The radius of the rotary valve 80 L; the length of the arm up to the point A of the driving force.

In order to rotate the rotary valve 80,
Is the torque due to the driving force is M_rAnd F ₀Caused by
Friction force μ · F (F is a vector) Total with torque
Need to balance. For this reason,

[0010]

[Equation 1]

Where F ₀ is the resultant force of F and μ · F,

[0012]

[Equation 2]

Therefore,

[0014]

(Equation 3)

Therefore, the equation (1) is

[0016]

[Equation 4]

[0017]

(Equation 5)

From the equation (2), in order to rotate the rotary valve 80,

[0019]

(Equation 6)

It turns out that it must be. (2)
Both sides of the equation are multiplied by L and transformed as follows.

[0021]

(Equation 7)

From equation (3), it can be seen how many times the drive torque L · F _s for driving the rotary valve 80 becomes M _r . From the equation (3), FIG. 20 shows the relationship between the friction coefficient μ and the torque coefficient L · F _s / M _r , with r being constant and L being a parameter. Here, L is ▽ as standard, × is 1.52 times of ▽, △ is 2.60 times of ▽, and ◇ is 3.25 of ▽.
Double, + is 4.23 times of ▽, and □ is 8.46 times of ▽.
From FIG. 20, when the arm length L is small, the driving torque L · F
_It can be seen that _s becomes large.

Even considering that the rotary valve 80 is pressed by the leaked gas pressure, the above equation (3) is similarly established. Therefore, also in this case, it is understood that the driving torque L · F _s becomes large when the arm length L is small. The driving force becomes minimum when the direction of F and the direction of gas pressure are the same, and the direction of F and the direction of gas pressure are 180 °.
When, that is, when they face each other, the driving force is maximized.

Therefore, in this compressor, there is an unavoidable misalignment e between the rotation center O of the drive shaft and the rotation center Q of the rotary valve 80, and the elongated hole 81 is formed in the radial direction to allow this misalignment e. Since it is slidable to the rotary valve 80, when transmitting the rotation to the rotary valve 80 by the drive shaft, a frictional force is generated between the rotary valve 80 and the shaft hole, and this frictional force causes seizure of the rotary valve 80. It can be seen that power loss was being generated.

According to the present invention, the seizure of the rotary valve is prevented and the smooth rotation of the drive shaft is allowed even when the lubricating oil around the rotary valve is scarce while allowing the unavoidable misalignment in manufacturing. Making possible is the problem to be solved.

[0026]

[Means for Solving the Problems]

(1) In the reciprocating compressor according to claim 1, the cylinder block having a plurality of bores around the shaft center, the drive shaft fitted and supported in the shaft hole of the cylinder block, and the drive shaft working together. Of the cylinder block that has a piston that is linearly moved in the bore in association with a swash plate in the crank chamber, a suction chamber that communicates with the shaft hole, and a discharge chamber that is formed in an outer region of the suction chamber. A housing for closing the end face is provided, a communication path is formed between each of the bores and the shaft hole, and a communication path of each bore in the suction stroke and the suction chamber are formed at the rear end of the drive shaft. In a reciprocating compressor in which a rotary valve having a suction passage that sequentially communicates is provided so as to be synchronously rotatable, an intermediate member having a diameter larger than that of the drive shaft is provided between the rotary valve and the drive shaft. A first fitting portion having a cylindrical surface parallel to the axis is provided at the front end of the rotary valve as far as possible from the axis. A second fitting portion that is provided at an eccentric position on the rear end of the drive shaft and has an opposing flat surface that is parallel to the shaft center; and the intermediate member is fitted with the second fitting portion. Second fitted portion that allows radial movement in the radial direction, and a first fitted portion that is provided in the extending direction of the second fitted portion and in which the first fitting portion is fitted in the rotational direction. And a part.

(2) A reciprocating compressor according to a second aspect is the reciprocating compressor according to the first aspect, in which a circumferential movement allowance due to rotation of the first fitted portion and a second fitted portion. The radial movement allowance of the joint portion is characterized by being at least twice the misalignment between the rotation center of the drive shaft, which is the shaft center, and the rotation center of the rotary valve. (3) In the reciprocating compressor according to claim 3, the cylinder block having a plurality of bores around the shaft center, the drive shaft fitted and supported in the shaft hole of the cylinder block, and the drive shaft cooperating with each other. Of the cylinder block that has a piston that is linearly moved in the bore in association with a swash plate in the crank chamber, a suction chamber that communicates with the shaft hole, and a discharge chamber that is formed in an outer region of the suction chamber. A housing for closing the end face is provided, a communication path is formed between each of the bores and the shaft hole, and a communication path of each bore in the suction stroke and the suction chamber are formed at the rear end of the drive shaft. In a reciprocating compressor in which a rotary valve having a sequentially communicating suction passage is provided so as to be synchronously rotatable, an intermediate member having a diameter larger than that of the drive shaft is fixed to a rear end of the drive shaft, and a front end of the rotary valve is provided. A first fitting portion having a cylindrical surface parallel to the axis is eccentric from the axis as much as possible. It is provided at a position, the intermediary member, characterized in that the first fitted portion to allow movement of the rotational and radial directions first fitting portion is fitted is provided.

(4) A reciprocating compressor according to a fourth aspect is the reciprocating compressor according to the third aspect, in which the circumferential movement allowance and the radial movement allowance are caused by the rotation of the first fitted portion. The capacity is characterized by being more than twice the center misalignment between the rotation center of the drive shaft, which is the shaft center, and the rotation center of the rotary valve.

[0029]

[Action]

(1) In the reciprocating compressor according to claim 1, an intermediary member is provided between the rotary valve and the drive shaft. Further, a first fitting portion having a cylindrical surface parallel to the shaft center is provided at the front end of the rotary valve, and a second fitting portion having an opposing flat surface parallel to the shaft center is provided at the rear end of the drive shaft. . Then, by fitting the second fitting portion of the drive shaft to the second fitted portion of the intermediary member, and fitting the first fitting portion of the rotary valve to the first fitted portion of the intermediary member, A rotary valve is connected to the drive shaft.

When the drive shaft is driven around the center of rotation thereof in the above-mentioned coupling type compressor, the rotation of the drive shaft is prevented by the second fitting portion being fitted to the second fitted portion. Is transmitted to the intermediary member to rotate. Then, in the rotating intermediary member, the first fitted portion applies a driving force around the rotation center of the rotary valve to the first fitted portion of the rotary valve. Therefore, even if the rotation center of the drive shaft and the rotation center of the rotation valve are misaligned, the rotation valve rotates about its own rotation center. At this time, since the intermediary member swings with respect to the rotary valve with the center of the first fitting portion as the swing center, a phase shift occurs between the rotary valve and the rotation angle of the rotary valve.

Further, in this compressor, even when the center of rotation of the drive shaft and the center of rotation of the rotary valve are misaligned, the first member provided in the extending direction of the second fitted portion in the intermediate member.
Since the fitted portion is allowed to rotate relative to the first fitting portion of the rotary valve, under the regulation by the rotation of the first fitted portion,
The second fitted portion of the intermediary member is guided by the second fitted portion of the drive shaft and is allowed to move in the radial direction, and the misalignment is absorbed.

Further, in this compressor, the first fitting portion of the rotary valve is provided at a position as eccentric as possible from the shaft center, and is fitted by the first fitting portion and the first fitted portion. Since the intermediary member has a diameter larger than that of the drive shaft, the length of the arm up to the point of application of the drive force is increased and the drive torque is reduced. (2) In the reciprocating compressor according to claim 2, in the intermediary member, the second fitted portion allows the radial movement of the second fitted portion guided by the second fitting portion of the drive shaft to be more than twice the misalignment. Has been done. In addition, the first fitted portion rotates relative to the first fitted portion of the rotary valve, and the movement of the intermediary member in the circumferential direction due to the rotation of the first fitted portion is 2
More than doubled is allowed.

In this compressor, even when the center of rotation of the drive shaft and the center of rotation of the rotary valve have a misalignment, the misalignment can be reliably absorbed. (3) In the reciprocating compressor according to the third aspect, the intermediary member is fixed to the rear end of the drive shaft. Further, a first fitting portion having a cylindrical surface parallel to the axis is provided at the front end of the rotary valve. Then, the rotary valve is coupled to the drive shaft by fitting the first fitting portion of the rotary valve to the first fitted portion of the intermediary member.

When the drive shaft is driven around the center of rotation by the compressor of the coupling system, the rotation of the drive shaft is transmitted to the intermediate member fixed to the drive shaft, and the intermediate member rotates. Then, in the rotating intermediary member, the first fitted portion applies a driving force around the rotation center of the rotary valve to the first fitted portion of the rotary valve. Therefore, even if the rotation center of the drive shaft and the rotation center of the rotation valve are misaligned, the rotation valve rotates about its own rotation center. At this time, the intermediary member swings with respect to the rotary valve about the center of the first fitting portion that allows the radial movement of the first fitting portion as the swing center, so that there is a phase shift from the rotation angle of the rotary valve. Occurs.

Further, in this compressor, even when the center of rotation of the drive shaft and the center of rotation of the rotary valve are deviated from each other, the first fitted portion of the intermediate member and the first fitted portion of the rotary valve are Since the relative rotation and the movement in the radial direction are allowed, the first fitted portion of the intermediary member is guided by the first fitting portion of the rotary valve under the restriction of the rotation of the first fitted portion. Movement is allowed in the radial direction, and misalignment is absorbed.

Further, in this compressor, the first fitting portion of the rotary valve is provided at a position as eccentric as possible from the shaft center, and is fitted by the first fitting portion and the first fitted portion. Since the intermediary member has a diameter larger than that of the drive shaft, the length of the arm up to the point of application of the drive force is increased and the drive torque is reduced. (4) In the reciprocating compressor according to the fourth aspect, in the intermediary member, the first fitted portion is allowed to move in the radial direction of the first fitting portion of the rotary valve at twice or more the core misalignment. There is. Further, the first fitted portion rotates relative to the first fitted portion of the rotary valve, and the movement of the intermediary member in the circumferential direction due to the first fitted portion is allowed to be two times or more the misalignment.

In this compressor, even when the center of rotation of the drive shaft and the center of rotation of the rotary valve have a misalignment, the misalignment can be reliably absorbed.

[0038]

Embodiments 1 to 3 embodying the inventions of claims 1 to 4 will be described below with reference to the drawings. (Embodiment 1) A compressor according to Embodiment 1 is one in which claims 1 and 2 are embodied.

In this compressor, as shown in FIG. 1, the front housing 2 is joined to the front end side of the cylinder block 1 by a through bolt 21 and the rear housing 3 is connected to the rear end side of the cylinder block 1 via a valve plate 4. Through bolt 2
They are joined by 1. A drive shaft 6 extending in the direction of the axis O is housed in a crank chamber 5 formed by the cylinder block 1 and the front housing 2. The drive shaft 6 is supported in the shaft hole 2a of the front housing 2 via a shaft sealing device 7c and a bearing 7a, and
It is supported in the shaft hole 1a of the cylinder block 1 via a bearing 7b, and is rotatably supported by these. A plurality of cylinder bores 8 are formed in the cylinder block 1 at positions surrounding the drive shaft 6, and pistons 9 are inserted into the respective cylinder bores 8.

In the crank chamber 5, the rotor 10 is supported on the drive shaft 6 by the bearing 11 between the drive shaft 6 and the front shaft 2 so as to be rotatable in synchronism with the drive shaft 6, and the swash plate 12 is provided behind the rotor 10. Equipped. And the rotor 1
0 and the swash plate 12 have a pressing spring 13 interposed therebetween, and the pressing spring 13 biases the swash plate 12 toward the rear housing 3.

The swash plate 12 is formed with smooth ring-shaped sliding surfaces 12a on the outer peripheral sides of both end surfaces, and hemispherical shoes 14, 14 are in contact with the sliding surfaces 12a. The outer peripheral surfaces of these shoes 14, 14 are fitted to the ball bearing surface of the piston 9, and each piston 9 is housed in each cylinder bore 8 so as to be reciprocally movable. A pair of brackets 12b straddle the top dead center position T of the swash plate 12 on the inner dead center side and the rotor 10 side of the sliding surface 12a of the swash plate 12 with the drive shaft 6 interposed therebetween. It is projected in. One end of the guide pin 12c is fixed to each bracket 12b, and each guide pin 1
A sphere 12d is fixed to the other end of 2c. Thus, in this compressor, the bracket 12b and the guide pin 1
A part of the hinge mechanism K is constituted by 2c and the sphere portion 12d.

Further, a through hole 20 is provided in the central area of the swash plate 12.
And the drive shaft 6 is inserted into the through hole 20. Further, a counterweight 15 is attached by a rivet (not shown) to the bottom dead center side of the inner region of the swash plate 12 and the rotor 10 side. This swash plate 12 is a counterweight 1.
The maximum inclination angle is maintained by the front end surface 12g of the through hole 20 side closer to the rear end surface 10a of the rotor 10 than the inner area where the No. 5 is mounted, while a part of the through hole 20 on the cylinder block 1 side is maintained. By contacting the circlip 22, the minimum inclination angle is maintained.

Further, a pair of support arms 17 constituting the remaining part of the hinge mechanism K are projected above the rotor 10 rearward in the direction of the axis O so as to face the guide pins 12c. A guide hole 17a is linearly provided at each tip of each support arm 17, and a spherical portion 12d of a guide pin 12c is rotatably and slidably inserted into each guide hole 17a. There is.

The rear housing 3 has an opening at the rear end face at the center and a shaft hole 1 of the cylinder block 1.
A suction chamber 30 communicating with a is provided, and a discharge chamber 31 is formed in the outer region of the suction chamber 30. A discharge port 32 communicating with the head of each bore 8 is provided through the valve plate 4, and a discharge valve and a retainer (not shown) are sandwiched between the discharge ports 32 of the discharge ports 31. An bleed passage (not shown) having a fixed throttle is provided between the crank chamber 5 and the suction chamber 30, and a control valve (not shown) is provided between the discharge chamber 31 and the crank chamber 5. An air supply passage (not shown) is provided. The pressure in the crank chamber 5 is controlled based on the cooling load by adjusting the inflow amount of the refrigerant gas from the discharge chamber 31 to the crank chamber 5 by the control valve provided in the rear housing 3.

Further, the cylinder block 1 is formed with a radial conduction path 33 for conducting the head of each bore 8 and the shaft hole 1a, and the rotary valve 40 is coupled to the rear end of the drive shaft 6 in the shaft hole 1a. Has been done. That is, as shown in FIG.
A convex portion 60 as a second fitting portion is projectingly provided at the rear end of the drive shaft 6, and the convex portion 60 has an opposing flat surface 60a parallel to the axis O as shown in FIGS. , 60b are formed. Further, as shown in FIG. 2, a flange 40a is projected at the front end of the rotary valve 40 in parallel with the shaft center O, and a pin is provided in the inner region of the flange 40a at a position eccentric from the shaft center O as much as possible. The hole 41 is recessed. The pin 42 as the first fitting portion is press-fitted into the pin hole 41, and the pin 42
Has a cylindrical surface parallel to the axis O on the outer circumference.

Between the rotary valve 40 and the drive shaft 6, a disc-shaped intermediate member 50 having a larger diameter than that of the drive shaft 6 is provided via a disc spring 70 between the rotary shaft 40 and the drive shaft 6. . In the intermediate member 50, a long hole 51 as a second fitted portion into which the convex portion 60 is fitted is provided so as to penetrate through the central portion thereof, and the pin 4 is provided.
The round hole 52 as the first fitted portion into which 2 is fitted is the long hole 5
1 is provided so as to extend therethrough. Then, the convex portion 60 of the drive shaft 6 is fitted into the elongated hole 51 of the intermediary member 50, and the rotary valve 40
Pin 42 is fitted into the round hole 52 of the intermediate member 50.
The intermediary member 50 also functions as a seat for the disc spring 70.

Here, as shown in FIG. 3, the rotation center (axial center) O of the drive shaft 6 and the rotation center Q of the rotary valve 40 have a center misalignment e due to an unavoidable manufacturing error. . Then, in the intermediary member 50, the elongated hole 51 is guided by the convex portion 60 of the drive shaft 6 so as to be movable in the radial direction.
This radial movement is allowed to be twice or more the misalignment e until the convex portion 60 contacts both end surfaces of the elongated hole 51. Further, the round hole 52 is capable of rotating relative to the pin 42 of the rotary valve 40, whereby the intermediary member 50 can be moved in the circumferential direction. In other words, the intermediary member 50 can swing about the center P of the pin 42 as the swing center. The movement in the circumferential direction around the point P is allowed to be more than twice the misalignment e until the outer peripheral surface of the intermediary member 50 contacts the inner peripheral surface of the flange 40a of the rotary valve 40.

With this coupling method, as shown in FIG. 1, the cylindrical rotary valve 40 is coupled to the drive shaft 6, and a bearing 45 is provided at the rear end of the rotary valve 40. The rotary valve 40 is provided with an intake passage 43 that sequentially communicates each of the bores 8 in the intake stroke with the intake chamber 30, and also has a bypass passage 4 for returning the leaked refrigerant gas to each of the bores 8 in the intake stroke.
4 is engraved.

In the compressor configured as described above,
When the swash plate 12 rotates as the drive shaft 6 is driven, the shoes 14, 14 move back and forth while sliding on the sliding surface 12 a of the swash plate 12. Therefore, each piston 9 is connected to the cylinder bore 8
Reciprocates inside. The rotary valve 40 is synchronized with the drive shaft 6.
Rotates. Therefore, the refrigerant gas in the suction chamber 30 is sequentially sucked into each bore 8 through the suction passage 43 of the rotary valve 40 and the communication passage 33 of each bore 8 in the suction process. Thus
In each bore 8, the suction operation of the refrigerant gas is continued smoothly and stably, and the refrigerant gas can be compressed. For this reason, in this compressor, the pressure loss is extremely small, and sufficient volume efficiency can be maintained.

In the meantime, in this compressor in which the rotary valve 40 is connected to the drive shaft 6 by the above-mentioned coupling method, the rotation of the drive shaft 6 is transmitted by the rotary valve 40 as follows. That is, if the drive shaft 6 is driven from the state before starting shown in FIG.
As shown in FIG. 4 in which the rotation angle of 45 ° is 45 °, the convex portion 60 rotates about the rotation center O, and the convex portion 60 fits into the elongated hole 51, whereby the intermediate member 50 rotates. In the rotating intermediary member 50, the round hole 52 causes the pin 42 of the rotary valve 40 to apply a driving force around the rotation center Q of the rotary valve 40. Therefore, the rotary valve 40 rotates about its own rotation center Q even when it has the misalignment e.

At this time, the intermediary member 50 swings with respect to the rotary valve 40 around the point P as a swing center, so that the rotary valve 40 rotates more than the line connecting the rotary center O of the drive shaft 6 and the point P. Since the line connecting the center Q and the point P is located rearward in the rotation direction, the rotary valve 40 causes a phase delay with respect to the rotation angle of the drive shaft 6. Rotation angle of drive shaft 6 is 90 °, 135 °
The same applies to the states shown in FIGS. 5 and 6.

When the rotation angle of the drive shaft 6 is 180 °, as shown in FIG. 7, the rotation center Q of the rotary valve 40 is located on the line connecting the rotation center O of the drive shaft 6 and the point P. Even if the intermediary member 50 swings around the point P as the swing center, the rotary valve 4
0 produces almost no phase lag with the rotation angle of the drive shaft 6. After this, when the state where the rotation angle of the drive shaft 6 is 180 ° is passed, as shown in FIG. 8 where the rotation angle of the drive shaft 6 is 225 °, for example, as shown in FIG. Since the line connecting the rotation center Q of the rotary valve 40 and the point P is located ahead of the line connecting the
Causes a phase lead with the rotation angle of the drive shaft 6. The same applies to the states shown in FIGS. 9 and 10 in which the rotation angles of the drive shaft 6 are 270 ° and 315 °. And the rotation angle of the drive shaft is 3
It becomes 60 ° and these are repeated. These phase shifts have a relationship as shown in FIG.

Further, in this compressor, even when there is a misalignment e, the round hole 52 provided in the extending direction of the elongated hole 51 in the intermediary member 50 rotates relative to the pin 42 of the rotary valve 40, Since the movement of the intermediary member 50 in the circumferential direction is allowed by the above, under the regulation by the rotation of the round hole 52,
The elongated hole 51 of the intermediate member 50 is guided by the convex portion 60 of the drive shaft 6 and is allowed to move in the radial direction, and the misalignment e is absorbed.
Particularly, in this compressor, as shown in FIGS. 3 to 10, the radial movement of the intermediary member 50 and the circumferential movement around the point P are allowed to be more than twice the misalignment e. Because
Interference between the convex portion 60 and the long hole 51 and interference between the intermediary member 50 and the rotary valve 40 do not occur, and the misalignment e is reliably absorbed.

Further, in this compressor, the pin 42 of the rotary valve 40 is provided at a position as eccentric from the axis O as possible.
Intermediary member 50 fitted by this pin 42 and round hole 52
Has a larger diameter than the drive shaft 6, the arm length L up to the point of application of the drive force increases, and the drive torque is reduced.
Therefore, in this compressor, seizure of the rotary valve 40 can be prevented and the drive shaft can be prevented even when the lubricating oil around the rotary valve 40 is scarce while completely allowing the misalignment e which is unavoidable in manufacturing. 6 smooth rotation is possible.

(Embodiment 2) A compressor according to Embodiment 2 is an embodiment of claims 3 and 4. In this compressor, the drive shaft 6 and the rotary valve 40 are connected by the connecting method shown in FIG. That is, a small diameter portion 61 having a key groove 61a is provided at the rear end of the drive shaft 6, a shaft hole 55 that is aligned with the small diameter portion 61 is formed through the intermediate member 54, and the rotary valve is also provided. A long hole 56 as a first fitted portion into which the pin 42 of 40 is fitted is provided through. Then, the small diameter portion 61 of the drive shaft 6 is fitted into the shaft hole 55 of the intermediary member 54 to press the key 62 into the key groove 61a, and the intermediary member 54 is attached to the drive shaft 6.
Is fixed. Further, the pin 42 of the rotary valve 40 is connected to the intermediary member 5
4 is fitted in the long hole 56.

Here, in the intermediate member 54, the long hole 56
The pin 42 of the rotary valve 40 can rotate and move in the radial direction. In other words, the intermediary member 54 is capable of swinging with the center P of the pin 42, which moves in the radial direction within the elongated hole 56, as the swing center. The movement in the circumferential direction around the point P that is movable in the radial direction is performed by the intermediate member 54.
More than twice the misalignment e is allowed until the outer peripheral surface of the abutting contact with the inner peripheral surface of the flange 40a of the rotary valve 40.

Since the other structures are the same as those of the first embodiment, the same structures are designated by the same reference numerals and the description thereof will be omitted.
When the drive shaft 6 is driven around the rotation center O by the combined type compressor, the rotation of the drive shaft 6 is transmitted to the intermediate member 54 fixed to the drive shaft 6 by the key 62, and the intermediate member 54 rotates. To do. The elongated hole 56 of the rotating intermediary member 54 causes the driving force around the rotation center Q of the rotary valve 40 to act on the pin 42 of the rotary valve 40. Therefore, misalignment e
Even when the rotary valve 40 has the above-mentioned structure, the rotary valve 40 rotates about its own rotation center Q.

At this time, the intermediary member 54 oscillates around the center P of the elongated hole 56, which is capable of moving in the radial direction, as the oscillating center, so that a phase shift occurs with respect to the rotation angle of the drive shaft 6. In addition, in this compressor, even when there is misalignment e, the elongated hole 56 of the intermediary member 54 is allowed to move in the radial direction of the pin 42 of the rotary valve 40 at twice or more of the misalignment e. Since the movement of the intermediary member 54 in the circumferential direction about the point P is allowed to be more than twice the misalignment e, the oblong hole 56 of the intermediary member 54 is controlled by the rotation valve. Four
Guided by the pin 42 of 0, the movement in the radial direction is allowed, the interference between the intermediate member 54 and the rotary valve 40 does not occur, and the misalignment e
Is surely absorbed.

Further, in this compressor, the pin 42 of the rotary valve 40 is provided at a position as eccentric from the axis O as possible.
The intermediary member 54 fitted by the pin 42 and the long hole 56.
Has a larger diameter than the drive shaft 6, the arm length L up to the point of application of the drive force increases, and the drive torque is reduced.
Since other operations are the same as those of the first embodiment, description of the same operations will be omitted.

Therefore, also in this compressor, the same effect as that of the first embodiment can be obtained. (Embodiment 3) The compressor of Embodiment 3 also embodies claims 3 and 4. In this compressor, the drive shaft 6 and the rotary valve 4 are
0 and 0 are connected by the connection method shown in FIG.

That is, the cutout 58 as the first fitted portion into which the pin 42 of the rotary valve 40 is fitted to the intermediary member 57.
Is pierced. Then, the pin 42 of the rotary valve 40 is fitted into the notch 58 of the intermediary member 57. Here, in the intermediary member 57, the notch 58 is capable of rotating the pin 42 of the rotary valve 40 and moving in the radial direction. In other words, the intermediary member 57 is capable of swinging around the center P of the pin 42 that moves in the radial direction within the notch 58 as the swing center. The movement in the circumferential direction about the point P, which is movable in the radial direction, is misaligned e until the outer peripheral surface of the intermediate member 57 comes into contact with the inner peripheral surface of the flange 40a of the rotary valve 40.
More than twice the maximum is allowed.

Since other structures are the same as those of the second embodiment, the same structures are designated by the same reference numerals and the description thereof will be omitted.
Also in this compressor, the same operation and effect as those of the first embodiment can be achieved. In the compressor of the first embodiment, the convex portion 60 protruding from the drive shaft 6 is the second fitting portion, and the elongated hole 51 penetrating the intermediary member 50 is the second fitted portion. The intermediate member 50 is provided with a convex portion as a second fitted portion having an opposing flat surface parallel to the axis O, and a long hole as a second fitting portion for fitting the convex portion to the drive shaft 6 is formed. It can also be recessed.

Further, in the compressors of Examples 1 to 3 described above, the pin 42 protruding from the rotary valve 40 is used as the first fitting portion, and the round hole 52 penetrating the intermediary members 50, 54 and 57 has a long length. Hole 56,
Although the notch 58 is the first fitted portion, the intermediate member 50 is provided with a pin as the first fitted portion having a cylindrical surface parallel to the axis O, and the rotary valve 40 is fitted with this pin. It is also possible to form a round hole, a long hole, or a notch as the first fitting portion to be fitted.

[0064]

As described above in detail, since the reciprocating compressors according to claims 1 and 3 adopt the configurations described in each claim, while allowing an unavoidable misalignment in manufacturing. Even when the lubricating oil around the rotary valve is scarce, seizure of the rotary valve can be prevented and the drive shaft can smoothly rotate.

Further, since the reciprocating compressors according to claims 2 and 4 employ the configurations according to each claim, the effects of claims 1 and 3 can be more effectively achieved by completely absorbing the misalignment. Can be tightened.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment.

FIG. 2 is an exploded perspective view of relevant parts of the compressor according to the first embodiment.

FIG. 3 is a cross-sectional view of relevant parts of the compressor according to the first embodiment when the rotation angle of the drive shaft is 0 °.

FIG. 4 is a cross-sectional view of relevant parts of the compressor according to the first embodiment when the rotation angle of the drive shaft is 45 °.

FIG. 5 is a cross-sectional view of relevant parts of the compressor according to the first embodiment when the rotation angle of the drive shaft is 90 °.

FIG. 6 is a cross-sectional view of relevant parts of the compressor according to the first embodiment when the rotation angle of the drive shaft is 135 °.

FIG. 7 is a cross-sectional view of the essential parts of the compressor according to the first embodiment when the rotation angle of the drive shaft is 180 °.

FIG. 8 is a cross-sectional view of the main parts of the compressor according to the first embodiment when the rotation angle of the drive shaft is 225 °.

FIG. 9 is a cross-sectional view of the main parts of the compressor according to the first embodiment when the rotation angle of the drive shaft is 270 °.

FIG. 10 is a cross-sectional view of the essential parts of the compressor according to the first embodiment when the rotation angle of the drive shaft is 315 °.

FIG. 11 is a graph showing a relationship between a rotation angle of a drive shaft and a phase shift according to the compressor of the first embodiment.

FIG. 12 is a cross-sectional view of relevant parts of a compressor according to a second embodiment.

FIG. 13 is a cross-sectional view of relevant parts of a compressor according to a third embodiment.

FIG. 14 is related to a conventional compressor, and the rotation angle of the drive shaft is 0.
It is a principal part sectional view at the time of °.

FIG. 15 relates to a conventional compressor, and the rotation angle of the drive shaft is θ.
It is a principal part sectional view at the time of °.

FIG. 16 is related to the conventional compressor, and the rotation angle of the drive shaft is 4
It is a principal part sectional view at the time of 5 degrees.

FIG. 17 is related to a conventional compressor, and the rotation angle of the drive shaft is 9
It is a principal part sectional view at the time of 0 degree.

FIG. 18 relates to a conventional compressor, and the rotation angle of the drive shaft is 1
It is a principal part sectional view at the time of 35 degrees.

FIG. 19 is a cross-sectional view of relevant parts of a conventional compressor.

FIG. 20 is a graph showing a relationship between a friction coefficient and a torque coefficient.

[Explanation of symbols]

O ... Shaft center (rotation center of drive shaft) 1 ... Cylinder block 2, 3 ... Housing 8 ... Bore 1a
… Shaft hole 6… Drive shaft 5… Crank chamber 12
... Swash plate 9 ... Piston 30 ... Suction chamber 31
... Discharge chamber 33 ... Conducting path 40 ... Rotating valve 43
... Suction passages 50, 54, 57 ... Intermediary member 42 ... Pin (first
Fitting part 60 ... Convex part (second fitting part) 51 ... Long hole (second)
Fitted portion 52 ... Round hole (first fitted portion) 56 ... Long hole (first
Fitted part) 58 ... Notch (first fitted part) Q ... Rotation center of rotary valve e ... Misalignment

Claims (4)

[Claims] 1. A cylinder block having a plurality of bores around an axis, a drive shaft fitted and supported in a shaft hole of the cylinder block, and a swash plate in a crank chamber cooperating with the drive shaft. And a housing that has a suction chamber communicating with the shaft hole and a discharge chamber formed in an outer region of the suction chamber and closes an end surface of the cylinder block. A rotary passage having a passage formed between the bore and the shaft hole, and a suction passage at the rear end of the drive shaft for sequentially connecting the passage of the bore in the suction stroke and the suction chamber. In a reciprocating compressor provided so as to be rotatable synchronously, an intermediate member having a diameter larger than that of the drive shaft is provided between the rotary valve and the drive shaft, and the shaft center is provided at a front end of the rotary valve. A first fitting part having a cylindrical surface parallel to the shaft is provided at a position as eccentric as possible from the axis. A second fitting portion having an opposing flat surface parallel to the shaft center is provided at the rear end of the drive shaft, and the intermediary member is moved in the radial direction by fitting the second fitting portion. It has a second fitted portion that allows and a first fitted portion that is provided in the extending direction of the second fitted portion and that the first fitting portion is fitted in the rotation direction. Characteristic reciprocating compressor. 2. The permissible movement amount in the circumferential direction by the rotation of the first fitted part and the radial movement allowance of the second fitted part are the rotation center of the drive shaft, which is the shaft center, and the rotary valve. 2. The reciprocating compressor according to claim 1, wherein the center misalignment with the rotation center is 2 times or more. 3. A cylinder block having a plurality of bores around an axis, a drive shaft fitted and supported in a shaft hole of the cylinder block, and a swash plate in a crank chamber cooperating with the drive shaft. And a housing that has a suction chamber communicating with the shaft hole and a discharge chamber formed in an outer region of the suction chamber and closes an end surface of the cylinder block. A rotary passage having a passage formed between the bore and the shaft hole, and a suction passage at the rear end of the drive shaft for sequentially connecting the passage of the bore in the suction stroke and the suction chamber. In a reciprocating compressor provided so as to be rotatable synchronously, an intermediate member having a diameter larger than that of the drive shaft is fixed to a rear end of the drive shaft, and a cylinder parallel to the shaft center is provided at a front end of the rotary valve. A first fitting portion having a surface is provided at a position as eccentric as possible from the axis, and The reciprocating compressor, wherein the interposition member is provided with a first fitted portion which is fitted with the first fitting portion and allows rotation and radial movement. 4. The permissible movement in the circumferential direction and the permissible movement in the radial direction due to the rotation of the first mating portion is 2 times the misalignment between the rotation center of the drive shaft, which is the shaft center, and the rotation center of the rotary valve. The reciprocating compressor according to claim 3, wherein the reciprocating compressor is at least double in number.