JP2004027871A - Piston type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a piston type compressor capable of suppressing local friction between a single head piston and a cylinder bore, reducing piston vibrations, and preventing the leakage of blow-by gas and lubricating oil. <P>SOLUTION: The piston type compressor comprises the cylinder bore 131, the single head piston 132 linearly reciprocating in the cylinder bore 131, and a movement converting mechanism converting rotating movement of a driving source to reciprocating linear movement of the single head piston 132. A tilting regulating member 153 is provided, which regulates tilting of the single head piston 132 by holding at least a part of the single head piston 132 on an inner peripheral surface of the cylinder bore 131. Therefore, the local friction between the single head piston 132 and the cylinder bore 131 is suppressed, and the piston vibrations are reduced. Furthermore, the leakage of the blow-by gas and the lubricating oil is suppressed. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a piston type compressor that compresses a refrigerant by reciprocating a single-headed piston.
[0002]
[Prior art]
Hitherto, as this type of piston type compressor, for example, a single-headed piston type swash plate type compressor described in Japanese Patent Application Laid-Open No. 5-302570 has been proposed.
[0003]
This single-headed piston type swash plate type compressor has a cylinder bore formed in a plurality of sections in a cylinder block, a single-headed piston accommodated in each cylinder bore so as to be able to reciprocate linearly, and a single-headed rotational movement of a drive source installed in a crank chamber. A motion conversion mechanism for converting the reciprocating linear motion of the piston. This motion conversion mechanism includes a swash plate mounted on a rotary drive shaft, and a pair of shoes provided on a bridge portion of a single-headed piston, and a peripheral portion of the swash plate is fitted so as to slide between the shoes. . Here, when the drive shaft rotates, the swash plate rotates in an inclined state, and accordingly, the single-headed piston reciprocates up and down.
[0004]
In such a single-headed piston type swash plate type compressor, when the single-headed piston reciprocates linearly, concentrated pressing force is applied toward the inner peripheral surface of the end of each cylinder bore on the crank chamber side. This operation will be described with reference to FIG. 12. When the swash plate 1 rotates and the single-headed piston 2 starts the compression stroke, a compression force F1 and a component force F2 orthogonal thereto act on the swash plate 1, and the single-headed piston 2 is moved as shown in FIG. Receives a clockwise moment M as shown in FIG. This moment M acts as a concentrated pressing force FM1 at a contact portion P1 between the outer peripheral surface of the single-headed piston 2 and the inner peripheral surface at the end of the cylinder bore 3 on the crank chamber side. For this reason, there is a problem that the inner peripheral surface of the cylinder bore 3 and the outer peripheral surface of the single-headed piston 2 are worn out early. Incidentally, in the suction process of the single-headed piston 2, the single-headed piston 2 tilts in the opposite direction as shown by a two-dot chain line and the single-headed piston 2 comes into contact with the inner peripheral surface of the cylinder bore 3, but the pressure in the cylinder bore 3 is compared with that during the compression stroke. Therefore, the concentrated pressing force is not so large.
[0005]
Here, when the wear mark 2a of the single-headed piston 2 was examined, as shown in FIG. 13 (a), the wear mark 2a was left obliquely from the base side of the single-headed piston 2 toward the tip thereof. In the compression stroke of the piston 2, as shown by the arrow A in FIG. 13B, on the other hand, in the suction process of the single-headed piston 2, as shown by the arrow B, the pressing surface between the single-ended piston 2 and the cylinder bore 3 changes. .
[0006]
Therefore, in order to solve the problem of abrasion during the compression step of the single-headed piston 2, the single-headed piston type swash plate type compressor described in the above publication, as shown in FIG. A structure is employed in which an annular elastic member 5 is fitted into the cylinder block 4 on the inner peripheral surface at the end of the crank chamber. As a result, the concentrated pressing force FM1 is applied to the elastic member 5, but the elastic force prevents the single-headed piston 2 from being worn.
[0007]
[Problems to be solved by the invention]
However, in the piston-type compressor described in the above publication, the inclination angle of the single-headed piston 2 is increased (for example, 3.5 °) due to the elastic deformation of the elastic member 5, and the concentrated pressing force is further increased. Thereby, as indicated by the arrow in FIG. 14A, the amount of blow-by gas flowing from the cylinder bore 3 to the crank chamber increases, thereby reducing the compression efficiency or lubricating from the crank chamber toward the cylinder bore 3. There has been a problem that the amount of oil increases and the lubricating property of a sliding device installed in the crankcase is impaired.
[0008]
The elastic deformation of the elastic member 5 causes the single-headed piston 2 to hit the inner peripheral surface of the cylinder bore 3 in the vicinity of the elastic member 5, and the single-headed piston 2 may be worn out. Wear may also occur on the tip side.
[0009]
In order to solve this problem, as shown in FIG. 14 (b), a structure has been proposed in which the axial width of the elastic member 5 is further increased, and the elastic member 6 is also attached to the tip end side of the single-headed piston 2. However, in this case, there is a problem that the inclination angle of the single-headed piston 2 is further increased (for example, 4.4 °), and the escape amount of the blow-by gas and the lubricating oil from the crankcase further increases.
[0010]
Further, as the inclination angle of the single-headed piston 2 increases, the swing of the single-headed piston 2 generated in the compression stroke and the suction process increases, and the vibration of the piston increases accordingly. .
[0011]
In view of the above-mentioned conventional problems, an object of the present invention is to not only suppress local friction between a single-headed piston and a cylinder bore, but also reduce piston vibration, further suppress blow-by gas and lubricating oil from coming off, and An object of the present invention is to provide a piston type compressor capable of dispersing a pressing force to a cylinder bore even when a piston and a cylinder bore are in sliding contact with each other.
[0012]
[Means for Solving the Problems]
In order to solve the above-mentioned problems, the present invention provides a cylinder bore defined in a cylinder block, a single-headed piston accommodated in a reciprocating linear motion in the cylinder bore, and a drive source installed in a crank chamber. And a motion conversion mechanism for converting the rotary motion of the single-headed piston into a reciprocating linear motion of the single-headed piston, wherein at least a part of the single-headed piston is held on the inner peripheral surface of the cylinder bore to regulate the tilt of the single-headed piston. The structure has a regulating member.
[0013]
According to the first aspect of the present invention, since the inclination of the single-headed piston is regulated by the inclination regulating member, the local friction between the single-headed piston and the cylinder bore is suppressed, the piston vibration is reduced, and the blow-by gas and the lubricating oil are further reduced. Omission is suppressed.
[0014]
According to a second aspect of the present invention, in the piston type compressor according to the first aspect, a fitting groove formed along a radial direction is formed on an inner peripheral surface of the cylinder bore, and the inclination restricting member fitted into the fitting groove is provided in the cylinder bore. Has a structure that slightly protrudes inward from the inner peripheral surface. According to the second aspect of the present invention, local friction between the one-sided piston and the cylinder bore is suppressed because the inclination regulating member protrudes from the inner peripheral surface of the cylinder bore. The inclination restricting member may be formed of a material having elasticity and wear resistance (the invention of claim 3).
[0015]
According to a fourth aspect of the present invention, in the piston type compressor according to any one of the first to third aspects, a plurality of inclination regulating members are provided at intervals in the axial direction of the cylinder bore. And the effect of restricting the inclination of the single-headed piston is further improved.
[0016]
The inclination restricting member may be formed in a ring shape as a whole (invention of claim 5), or may be formed in a semi-annular shape (invention of claim 6). When the annular or semi-annular inclination restricting member is formed to have an arc-shaped cross section so as to protrude inward, the sliding contact portion between the inclination restricting member and the single-headed piston is narrowed, and the frictional resistance is reduced. 7 invention).
[0017]
According to an eighth aspect of the present invention, in the piston type compressor according to any one of the second to seventh aspects, at least one of the opening end of the fitting groove and the crank chamber side end of the cylinder bore is provided with an outer peripheral surface of a single-headed piston whose inclination is restricted. It is formed so as to be in a sliding contact position. That is, the outer peripheral surface of the single-headed piston is in sliding contact with the inclination restricting member at at least one other location, and the sliding contact location is plural. Thereby, the pressing force applied from the single-headed piston is dispersed, and wear of the outer peripheral surface of the single-headed piston is prevented.
[0018]
According to the ninth aspect of the present invention, a tapered portion may be provided at the opening end of the fitting groove so that the inclination restricting member can be easily attached to the fitting groove. May be provided so that the single-headed piston is easily accommodated and arranged in the cylinder bore.
[0019]
According to an eleventh aspect of the present invention, in the piston type compressor according to any one of the first to ninth aspects, the piston type compressor has a structure in which a piston ring is provided on a tip side of a single-headed piston. Thereby, oil is held between the inclination restricting member provided in the cylinder bore and the piston ring, and the one-sided piston slides smoothly.
[0020]
The refrigerant used in the piston-type compressor according to the present invention is not limited to Freon, ammonia and the like, but also includes hydrocarbon refrigerants such as carbon dioxide, propane and butane (the invention of claim 12).
[0021]
BEST MODE FOR CARRYING OUT THE INVENTION
1 to 4 show a piston type compressor according to a first embodiment of the present invention. FIG. 1 is a cross-sectional view of the piston type compressor, and FIG. 2 is a cross-sectional view showing a state in which a single-headed piston is housed in a cylinder bore. FIG. 3 is a perspective view showing an inclination restricting member, and FIG. 4 is a sectional view showing a main part of the first embodiment. In the present embodiment, a single-headed piston type swash plate type compressor (hereinafter, referred to as a compressor) will be described as an example among the piston type compressors.
[0022]
First, the overall structure of the compressor 10 will be described with reference to FIG. The compressor 10 has a rear housing 11 and a front housing 12, and a cylinder block 13 is formed on the front housing 12 on the rear housing 11 side. A plurality of cylindrical cylinder bores 131 are formed in the cylinder block portion 13, and each of the cylinder bores 131 accommodates a single-headed piston 132 such that the piston 132 can reciprocate linearly. A refrigerant suction chamber 111 and a discharge chamber 112 are formed in the rear housing 11. Each of the chambers 111 and 112 communicates with a cylinder bore 131 via a valve body. Inflated. A rotating shaft 121 protruding from the cylinder block 13 to the outside of the front housing 12 penetrates the front housing 12. The rotating shaft 121 is supported by bearings 133 and 122 interposed in the cylinder block 13 and the front housing 12, and the tip thereof is connected to the electromagnetic clutch 14. The electromagnetic clutch 14 has a pulley 141 connected to a belt of an automobile engine (not shown), and a rotational force output from the engine is transmitted to the rotating shaft 121 through the electromagnetic clutch 14.
[0023]
The rotary motion transmitted to the rotary shaft 121 is converted into a reciprocating linear motion by the motion converting mechanism 15 installed in the crank chamber 123 of the front housing 12. That is, the motion conversion mechanism 15 is interposed in the rotor 151 fixed to the rotating shaft 121, the connecting portion 152 connected to the rotor 151, the swash plate 153 fixed to the connecting portion 152, and the bridge portion 132 a of the single-headed piston 132. The swash plate 153 is slidably sandwiched between the peripheral edges of the swash plate 153. Here, when the rotating shaft 121 performs a rotating motion, the rotor 151 and the connecting portion 152 rotate, and accordingly, the swash plate 153 rotates. Since the swash plate 153 rotates while being inclined with respect to the rotation shaft 121, the single-headed piston 132 reciprocates in a linear direction by an amount corresponding to the inclination width of the swash plate 153. In this motion conversion mechanism 15, the inclination angle of the swash plate 153 changes in accordance with the pressure difference between the pressure in the crank chamber 123 and the suction pressure in the cylinder bore 131, so that the stroke of the single-headed piston 132 can be changed. .
[0024]
The compressor structure as described above is the same as the conventional compressor structure, and the compressor 10 according to the present invention is provided with the inclination regulating member 20 on the inner peripheral surface of the cylinder bore 131. The structure of the inclination restricting member 20 will be described with reference to FIGS.
[0025]
That is, the inclination restricting member 20 is formed by an annular plate as shown in FIG. The inclination restricting member 20 has an arc-shaped cross section so as to protrude inward. The inclination restricting member 20 is made of, for example, ethylene tetrafluoride resin (PTFE), which has excellent wear resistance and is more elastic than the single-ended piston 132 made of an aluminum alloy. Of course, an iron-based or aluminum-based material having excellent elasticity may be used as the base material, and this may be coated with a wear-resistant material such as PTFE.
[0026]
The inclination restricting member 20 is disposed on the inner peripheral surface of the cylinder bore 131 near the crank chamber 123 as shown in FIGS. That is, an annular fitting groove 134 is formed on the inner peripheral surface of the cylinder bore 131, and the inclination restricting member 20 is fitted into the fitting groove 134. Further, as shown in FIG. 4, the width dimension of the fitting groove 134 is slightly larger than the diameter dimension of the inclination regulating member 20 to allow deformation of the inclination regulating member 20, and the groove depth dimension of the fitting groove 134 is the same. As shown in FIG. 4, it is designed to be shallower than the outer peripheral surface radius of the inclination restricting member 20 so that the center of the inner surface of the inclination restricting member 20 projects slightly inward from the inner peripheral surface of the cylinder bore 131. Further, a tapered portion 134 a having an opening diameter increasing toward the inside of the cylinder bore 131 is formed at the opening end of the fitting groove 134. As shown in FIG. 4, a tapered portion 131a whose opening diameter increases toward the crank chamber 123 is also formed in the opening of the cylinder bore 131 on the crank chamber side.
[0027]
According to the present embodiment, when the swash plate 153 rotates and the single-headed piston 132 starts the compression stroke, the compression force and the orthogonal force are applied to the operation of converting the rotation of the rotary shaft 121 into the reciprocating linear movement of the single-headed piston 132. As a result, a single-headed piston 132 receives a moment in the same manner as in the conventional example, and is brought into an inclined state as shown in FIG.
[0028]
Here, in the compressor 10 according to the present embodiment, as described above, the annular fitting groove 134 is formed in the inner peripheral surface of the cylinder bore 131, and the inclination regulating member 20 is fitted into the fitting groove 134, Since the regulating member 20 holds the outer peripheral surface of the single-headed piston 132 as shown in FIG. 4, the inclination angle of the single-headed piston 132 is reduced (0.78 °). Therefore, sliding contact between the single-headed piston 20 and the cylinder bore 131 is prevented, and local wear of the single-headed piston 20 is prevented.
[0029]
Further, the inclination angle of the single-headed piston 20 is reduced, and the swing range of the single-headed piston 20 in the lateral direction is reduced, so that the piston vibration is also reduced.
[0030]
Further, the inclination restricting member 20 also functions as a member that restricts the blow-by gas and the lubricating oil from coming off.
[0031]
Furthermore, since the tapered portion 134a is formed at the opening end of the fitting groove 134, the inclination restricting member 20 can be easily attached to the fitting groove 134, and the tapered portion is formed at the crank chamber side opening of the cylinder bore 131. Since the portion 131a is formed, the single-headed piston 132 can be easily housed and disposed in the cylinder bore 131.
[0032]
In the present embodiment, the width of the fitting groove 134 is slightly larger than the diameter of the inclination restricting member 20 to allow the deformation of the inclination restricting member 20. However, when the deformation of the single-headed piston 132 is not so large, Alternatively, the width of the fitting groove 134 and the diameter of the inclination restricting member 20 may be the same. The refrigerant used in the compressor 10 according to the present embodiment is not limited to Freon, ammonia, and the like, and may be a hydrocarbon refrigerant such as carbon dioxide, propane, and butane.
[0033]
FIG. 5 shows a second embodiment of the present invention. The same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
[0034]
In the first embodiment, the inner diameter of the cylinder bore 131 is formed to be the same with the fitting groove 134 interposed therebetween.
[0035]
On the other hand, in the present embodiment, one end 134b (the end of the fitting groove 134 on the crank chamber side (including the crank chamber side opening 131b of the cylinder bore 131)) of the opening end of the fitting groove 134 and the other end. (The end of the fitting groove 134 on the head side of the cylinder bore 131) is formed to have a different inner diameter.
[0036]
That is, the diameter of one end 134b is larger than the diameter of the other end 134c (increased by the radius D1). As a result, the pressing force applied to the cylinder bore 131 from the single-headed piston 132 is distributed to the two portions of the inclination regulating member 20 and the crank chamber-side opening 131b of the cylinder bore 131, so that the outer peripheral surface of the single-headed piston 132 is prevented from being worn. Note that other configurations, operations, and the like are the same as those in the first embodiment, and a description thereof will not be repeated.
[0037]
FIG. 6 shows a third embodiment of the present invention. The same components as those in the second embodiment are denoted by the same reference numerals, and the description thereof is omitted.
[0038]
In the second embodiment, the diameter of one end 134b of the opening end of the fitting groove 134 is larger than the diameter of the other end 134c.
[0039]
On the other hand, in the present embodiment, contrary to the second embodiment, the diameter of one end 134b is smaller than the diameter of the other end 134c (smaller by the radius D2). As a result, the pressing force applied from the single-headed piston 132 to the cylinder bore 131 is distributed to the three portions of the inclination restricting member 20, the crank chamber-side opening 131 b of the cylinder bore 131, and the other end 134 c. Wear is prevented. Note that other configurations, operations, and the like are the same as those in the first embodiment, and a description thereof will not be repeated.
[0040]
As described above, in the second embodiment and the third embodiment, the diameter of one end 134b (including the crank chamber side opening 131b of the cylinder bore 131) of the fitting groove 134 and the diameter of the other end 134c are different. The single-headed piston 132 is pressed at a plurality of places, but how the inner diameter difference between the ends 134b and 134c is set depends on the gap size between the single-headed piston 132 and the cylinder bore 131, the inclination angle of the single-headed piston 132, What is necessary is just to comprehensively determine the size of the inward projection of the inclination regulating member 20 and the like, and to select an appropriate inner diameter difference as appropriate.
[0041]
FIG. 7 shows a fourth embodiment of the present invention, and the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted.
[0042]
Although the compressor 10 shown in FIG. 1 employs a front housing 12 integrally formed with a cylinder block 13, some compressors have the cylinder block 13 formed separately from the front housing 12. In such a compressor (not shown), a gasket is interposed at a connection portion between the cylinder block and the front housing.
[0043]
Further, since the portion where the concentrated pressing force of the single-headed piston 20 is applied is the crank chamber side opening 131b of the cylinder bore 131, the inclination restricting effect is most exhibited when the inclination restricting member 20 is installed in the portion where the concentrated pressing force is applied.
[0044]
Based on the above points, the fourth embodiment adopts a structure in which the fitting groove 135 is formed in the crank chamber side opening, and the inclination regulating member 20 fitted in the fitting groove 135 is installed with the screw-fixed gasket 136. . By employing this structure, the inclination angle of the single-headed piston 20 could be further reduced (0.18 °). Note that other configurations, operations, and the like are the same as those in the first embodiment, and a description thereof will not be repeated.
[0045]
FIG. 8 shows a fifth embodiment of the present invention. The same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
[0046]
In the first to fourth embodiments, the fitting grooves 134 and 135 are formed at one position of the cylinder bore 131. On the other hand, in the present embodiment, a plurality of fitting grooves 134 are provided at intervals in the axial direction of the cylinder bore 131, and the inclination regulating member 20 is provided in each of the fitting grooves 134.
[0047]
According to the present embodiment, since the effect of restricting the inclination of the single-headed piston 20 is exerted at a plurality of locations on the single-headed piston 20, the inclination angle of the single-headed piston 20 is further reduced (0.1 °). Note that other configurations, operations, and the like are the same as those in the first embodiment, and a description thereof will not be repeated.
[0048]
FIG. 9 shows a sixth embodiment of the present invention. The same components as those in the first embodiment are represented by the same reference numerals, and the description thereof is omitted.
[0049]
In the first to fifth embodiments, the inclination of the single-headed piston 132 is regulated by the inclination regulating member 20. On the other hand, in the present embodiment, in addition to the inclination restricting member 20, the inclination of the single-headed piston 132 is restricted by the piston ring 132b. Here, the piston ring 132b is installed near the head of the single-headed piston 132. This is because the inclination regulating member 20 and the piston ring 132b do not collide with each other, and the interval between the inclination regulating member 20 and the piston ring 132b is increased to promote the inclination regulating effect.
[0050]
According to the present embodiment, not only is the inclination of the single head piston 132 restricted by both the inclination restricting member 20 and the piston ring 132b, but also the lubricating oil 137 is held between the inclination restricting member 20 and the piston ring 132b, and The slidability of the piston 20 is improved.
[0051]
Further, the inclination restricting member 20 can suppress the intrusion of the lubricating oil from the crank chamber 123 side, while the piston ring 132b can suppress the intrusion of the blow-by gas. Note that other configurations, operations, and the like are the same as those in the first embodiment, and a description thereof will not be repeated.
[0052]
Although the first to sixth embodiments have been described above, instead of the inclination restricting member 20 used here, as shown in FIG. 10, an inclination restricting member 21 partially cut in the axial direction is used. You may. When the inclination restricting member 21 is employed, the inclination restricting member 21 can be easily fitted into the fitting groove 134 by the elasticity of the inclination restricting member 21 in the circumferential direction. Further, as shown in FIG. 11, a semi-annular inclination restricting member 22 may be used. The inclination of the single-headed piston 132 during the compression stroke is repeated in a similar inclined state. Therefore, even if the semi-annular inclination restricting member 22 is installed so as to correspond to the position receiving the pressing force from the single head piston 132, the inclination of the single head piston 20 can be effectively restricted.
[0053]
【The invention's effect】
As described above, according to the present invention, since the inclination of the single-headed piston is regulated by the inclination regulating member, the local wear of the single-headed piston and the cylinder bore is suppressed, and the piston vibration is reduced. Lubricating oil is prevented from coming off.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a piston compressor. FIG. 2 is a cross-sectional view showing a state in which a single-headed piston is housed in a cylinder bore according to a first embodiment. FIG. 3 is a perspective view showing an inclination restricting member of the first embodiment. FIG. 4 is a cross-sectional view showing a main part of the first embodiment. FIG. 5 is a cross-sectional view showing a main part of the second embodiment. FIG. 6 is a cross-sectional view showing a main part of the third embodiment. FIG. 8 is a sectional view showing a state where a single-headed piston is housed in a cylinder bore according to an embodiment. FIG. 8 is a sectional view showing a state where a single-headed piston is housed in a cylinder bore according to a fifth embodiment. FIG. 9 is a view showing a cylinder bore according to a sixth embodiment. FIG. 10 is a perspective view showing a modification of the inclination restricting member. FIG. 11 is a perspective view showing another modification of the inclination restricting member. FIG. 12 is a pressing operation of the single head piston. Fig. 13: Single-headed piston with wear marks Figure 14 is a sectional view showing a housing condition of the single-headed pistons to conventional cylinder bore in which the elastic member is mounted EXPLANATION OF REFERENCE NUMERALS shown
DESCRIPTION OF SYMBOLS 10 ... Single head piston type swash plate type compressor, 12 ... Front housing, 13 ... Cylinder block part, 15 ... Motion conversion mechanism, 20, 21, 22 ... Inclination regulating member, 123 ... Crank chamber, 131 ... Cylinder bore, 132 ... Single head piston , 132b ... piston rings, 134, 135 ... fitting grooves, 131a, 134a ... taper portions.

Claims (12)

A cylinder bore defined in the cylinder block, a single-headed piston accommodated in the cylinder bore for reciprocating linear motion, and a motion installed in the crank chamber for converting a rotational motion of a driving source into a reciprocating linear motion of the single-headed piston. In a piston type compressor equipped with a conversion mechanism,
A piston-type compressor, wherein an inclination restricting member that holds at least a part of the single-headed piston and restricts the inclination of the single-headed piston is provided on an inner peripheral surface of the cylinder bore. A fitting groove formed along the radial direction is formed in the inner peripheral surface of the cylinder bore, and the inclination restricting member fitted in the fitting groove slightly protrudes inward from the inner peripheral surface of the cylinder bore. The piston type compressor according to claim 1, wherein: 3. The piston type compressor according to claim 1, wherein the inclination restricting member is formed of a material having elasticity and wear resistance. The piston type compressor according to any one of claims 1 to 3, wherein a plurality of the inclination restricting members are provided at intervals in an axial direction of the cylinder bore. The piston type compressor according to any one of claims 1 to 4, wherein the inclination restricting member is formed in an annular shape. The piston type compressor according to any one of claims 1 to 4, wherein the inclination restricting member is formed in a semi-annular shape. The piston type compressor according to claim 5 or 6, wherein the inclination restricting member is formed to have an arc-shaped cross section so as to protrude inward. The at least one of the opening end of the fitting groove and the end of the cylinder bore on the crank chamber side is formed so as to be in a position where it is in sliding contact with the outer peripheral surface of the single-headed piston whose inclination is restricted. Item 8. The piston type compressor according to any one of items 7 to 9. The piston type compressor according to any one of claims 2 to 8, wherein an opening end of the fitting groove has a tapered portion having an opening diameter increasing toward the inside of the cylinder bore. The piston type compressor according to any one of claims 1 to 9, wherein the crank chamber side opening of the cylinder bore has a tapered portion on the periphery thereof, the opening diameter of which increases toward the crank chamber. . The piston type compressor according to any one of claims 1 to 9, wherein a piston ring is provided on a tip side of the single-headed piston. The piston type compressor according to any one of claims 1 to 11, wherein the refrigerant compressed in each of the cylinder bores is carbon dioxide or a hydrocarbon refrigerant.

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