KR101779714B1 - Device for compression of refrigerant with variable piston displacement - Google Patents

Abstract

The present invention relates to a coolant compressing device (1) with a variable stroke. The device includes a drive shaft (4) capable of rotating around a rotary shaft and a drive element (5, 5a, 5b). The drive shaft (4) and the drive element (5, 5a, 5b) are mechanically coupled to each other by a bolt (14) adjusted in a radial direction toward the drive shaft (4). The drive element (5, 5a, 5b) is arranged to be inclined at an angle to a plane adjusted in a direction vertical to an axial direction of the drive shaft (4) and rotates with the drive shaft (4). The inclined angle is changeable by a slide sleeve (17). The slide sleeve (17) is arranged to be able to move on the drive shaft (4) in the axial direction of the drive shaft (4). A movement passage of the slide sleeve (17) is limited by mechanical stopping units (20a, 20b) of the slide sleeve (17). In this case, the mechanical stopping units (20a, 20b) are formed within a section where the slide sleeve (17) comes into contact with the bolt. The purpose of the present invention is to provide the piston compressing device with the variable stroke of which a start angle of an inclined plate or a rotary loop is minimized.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a refrigerant compressor having a variable stroke volume,

The present invention relates to a refrigerant compressor with variable piston displacement. The apparatus includes a drive shaft and a drive element having a fixed reference point and rotatable about a rotation axis. Wherein the drive shaft and the drive element are mechanically coupled to each other through a bolt radially arranged in the direction of the drive shaft so that the drive element is inclined at an angle to the plane adjusted in a direction perpendicular to the axis of the drive shaft And is rotated together with the drive shaft. The inclination angle is variable and limited by a mechanical stop.

A compressor for mobile applications known in the prior art, in particular a compressor for a heating and cooling system of a vehicle (also referred to hereinafter as a refrigerant compressor) for transporting refrigerant through a refrigerant circulation system, Stroke piston compressor. In this case, the piston compressor is driven through a clutch or through a belt pulley and therefore without a clutch. In the case of a refrigerant compressor driven by a belt and a belt pulley in particular, the number of revolutions is regulated through the speed of the vehicle, in particular through the number of revolutions of the drive motor. The piston compressor with the variable stroke ensures a constant operation of the cooling and heating apparatus because the compressor has a constant or variable discharge capacity required regardless of the number of revolutions of the drive motor. For example, when the drive motor is operated in the idle state or at a low rotational speed, a large stroke volume is required. Alternatively, if the drive motor is operated at a high number of revolutions, the stroke frequency of the compressor becomes very high, consequently, the compressor has the same discharge capacity in a small stroke volume.

The piston compressor having the variable stroke volume is formed to have a swash plate or to have a swivel as a driving element. The piston stroke in the cylinder is regulated by the gas mass in the propulsion and working spaces of the cylinder and the dynamic mass force of the piston and swash plate or swing ring.

)하에 배치되어 있다. 구동 소자(5)의 가능한 각도 설정으로 인해, 구동 소자(5)의 주변부에 배치된 방사 방향의 위치들은 변동하는 축 방향 위치들을 포함할 수 있음으로써, 결과적으로 상기 피스톤(3)은 회전하는 구동 샤프트(4) 상에 고정된 구동 소자(5)에 의해 구동 샤프트(4)의 축 방향으로 왕복 운동할 수 있다. 그 결과 상기 구동 소자(5)는, 구동 샤프트(4)가 이러한 구동 샤프트(4)의 축에 대해 수직으로 형성된 평면에 대해 기울어져 있고, 구동 소자와 구동 샤프트(4)가 일체형으로 회전하도록 상기 구동 샤프트(4)에 고정되어 있다. 1 shows a prior art compressor 1 having a variable displacement volume which comprises a housing 2, a plurality of pistons 3, a drive shaft 4 and a drive element 5, . A plurality of cylinder bores 6, a crank chamber 7, a suction chamber 8 and a discharge chamber 9 are formed in the housing 2. The pistons 3 are radially fixed within the housing 2 so that they are accommodated in the respective one of the cylinder bores 6 and consequently the rotation of the driving shaft 4 and the driving element 5 The pistons 3 are slid to the periphery of the driving element 5 so that they can rotate in the axial direction in the cylinder bore 6 together with the rotation of the driving shaft 4 and the driving element 5, . The drive shaft 4 can be driven by a belt pulley 10 together with a rotor element 11 fixedly coupled to this drive shaft 4 and the drive shaft rotates within the crank chamber 7 So as to be supported by the housing (2). The driving element 5 which is supported on the other hand by the piston 3 and which is supported by the driving shaft 4 is supported at one angle to the axis of the driving shaft 4

). By virtue of the possible angular setting of the drive element 5, the radial positions located in the periphery of the drive element 5 can comprise varying axial positions, And can reciprocate in the axial direction of the drive shaft 4 by the drive element 5 fixed on the shaft 4. As a result, the drive element 5 is inclined with respect to a plane formed perpendicularly to the axis of the drive shaft 4, and the drive element 4 is rotated And is fixed to the drive shaft 4.

)과 최소 경사각(

) 사이의 영역 내에서, 구동 소자(5) 상에 제공되는 모멘트(moment)에 따라 이동한다. 이 경우, 상기 모멘트는 특히 크랭크 챔버(7) 내의 압력 및 실린더 보어(6) 내부의 압력에 기초한다. 압축기(1)의 행정 체적 및 그에 따른 변위 용적은 회전하는 구동 샤프트(4)에 대해 상대적인 구동 소자(5)의 각도(

) 변동에 의해 변경된다. 또한, 상기 압축기(1)는 구동 소자(5)의 경사각(

)을 변경하기 위해, 크랭크 챔버(7) 내부의 압력을 조절하기 위한 압력 조절 장치를 포함한다.In this case, the driving element 5 has a maximum inclination angle (

) And the minimum inclination angle (

In accordance with a moment provided on the driving element 5. In this case, In this case, the moment is based in particular on the pressure in the crank chamber 7 and on the pressure inside the cylinder bore 6. The stroke volume and the displacement volume of the compressor 1 are determined by the angle of the driving element 5 relative to the rotating drive shaft 4

). Further, the compressor (1) has an inclination angle < RTI ID = 0.0 >

) For adjusting the pressure inside the crank chamber (7).

)은 하우징(2) 내에 형성된 크랭크 챔버(7)의 내압 변동에 의해 조절된다. 특히, 상기 경사각(

)을 감소시키기 위해 상기 크랭크 챔버(7)의 내압은 증가한다. 경사각(

)을 확대하는 방향으로 구동 소자(5)를 기울이기 위해, 상기 구동 소자(5)는 최대 경사각(

) 방향으로 이동한다. 이때 상기 크랭크 챔버(7)의 내압은 줄어든다. 상기 최대 경사각(

)으로 구동 소자(5)를 복귀시키기 위해, 구동 샤프트(4)의 축에 대해 수직으로 조정되어 있는 평면을 기준으로 측정했을 때 최소 경사각(

)은 0° 범위 내에 놓여서는 안 된다. 구동 소자(5)의 최소 경사각(

)이 0° 범위 내에 조절되면, 단지 최소의 압축이 이루어지거나 또는 압축이 전혀 이루어지지 않게 되고, 그 결과 최대 경사각(

)을 얻거나 또는 구동 소자(5)의 경사각(

)을 확대하기에 충분한 크기의 압축 반력도 생성되지 않는다. 따라서 상기 구동 소자(5)는 최대 경사각(

)으로 복귀할 수 없다.The inclination angle of the driving element 5

Is controlled by the pressure fluctuation of the crank chamber 7 formed in the housing 2. In particular,

The internal pressure of the crank chamber 7 is increased. Inclination angle

, The driving element 5 is inclined at a maximum inclination angle < RTI ID = 0.0 >

) Direction. At this time, the internal pressure of the crank chamber 7 is reduced. The maximum inclination angle (

) Of the driving shaft 4 in the direction perpendicular to the axis of the driving shaft 4 in order to return the driving element 5 to the minimum inclination angle

) Shall not be within 0 ° range. The minimum inclination angle of the driving element 5

) Is adjusted within the range of 0 DEG, only minimal compression or no compression occurs, resulting in a maximum inclination angle < RTI ID = 0.0 >

Or the inclination angle of the driving element 5

A compression reaction force of a sufficient magnitude is not generated. Therefore, the driving element 5 has a maximum inclination angle (

). ≪ / RTI >

In order for the compressor to start safely under the limiting conditions necessary for mobility applications, minimum starting angles of the drive elements, i. E. The swash plate and swivel ring, are required. In this case, the starting angle value depends on the necessary starting limit condition, in particular the number of revolutions. In the case of compressors driven through belt pulleys, on the one hand the starting angle depends, for example, on the maximum permissible conveying capacity in a switched off compressor, while on the other hand the minimum starting angle is mainly dependent on the traction It affects the towing capacity and is minimized for efficient reasons, resulting in a fairly limited range of starting angle values. In the case of a compressor with a swash plate, the starting angle can be adjusted through a fixed stop in the drive system. The starting angles of some compressors with swash plates, in particular those with swivel rings, are determined by the dynamic mass force of the piston and swash plate or swivel, and by the starting spring and, optionally, .

A ramp compressor is known from European Patent Application EP 0 953 765 A2. The swash plate moves in accordance with the moment within the region between the maximum inclination angle position and the minimum inclination angle position. In this case, the minimum inclination angle is smaller than the critical angle. The critical angle is determined by the lower limit of the inclined angle range in which the swash plate can move by the reaction force of the pressure applied to the piston to enlarge the angle. When the inclination angle of the swash plate is smaller than the critical angle, a compressive stress element formed as a recoil spring applies compressive stress to the swash plate to enlarge the inclination angle. The swash plate is also formed and arranged so that, when the swash plate arranged at an inclination angle smaller than the critical angle is rotated, an additional moment generated based on the inertia of the object by the swash plate is provided on the swash plate have. The inclination angle of the swash plate increases from the minimum inclination angle by the interaction of the additional moment and the moment generated by the reaction spring force.

In the case of piston compressors having a variable stroke belonging to the prior art, regardless of whether the starting angle is also adjusted depending on the mass force of the swash plate or swing ring, and depending on the pistons with or without the starting spring and recoil spring A fixed mechanical stop for the swash plate or swivel ring is provided as a drive element in the drive system.

2 shows in greater detail the drive shaft 4 of the prior art swash plate compressor with the rotor element 11 and the drive element 5, in particular the swash plate 5a. In this case, a fixed mechanical stop is provided within the slot-shaped feature 13 formed in the engaging element 12 disposed between the swash plate 5a and the rotor element 11 fixedly coupled to the drive shaft 4 Respectively. The rotor element 11 fixedly coupled to the drive shaft 4 is also denoted as a carrier and the engaging element 12 is also denoted as a follower joint.

3 shows the arrangement of a prior art fixed mechanical stop 20 ', which is also provided for a compressor with a rotating ring 5b, but which is also suitable for a compressor with a swash plate as a drive element. A bolt 14 (also referred to as a pin or a rotating pin) radially disposed on the drive shaft 4 has a joint head 15 as a mechanical connection between the drive shaft 4 and the rotation ring 5b, Into the engaging space 16 of the rotation ring 5b opened in the direction of the drive shaft 4. [ The inclination angle of the rotation ring 5b is realized through a slide sleeve 17 which is arranged movably on the drive shaft 4 in the axial direction of the drive shaft 4. [ The slide sleeve 17 is mechanically coupled to the rotation ring 5b via two joint pins (not shown), and the rotation ring is rotatably disposed in a direction perpendicular to the drive shaft 4. The fixed mechanical stop 20 'is formed in the drive shaft 4 as a heel 18 which limits the travel path of the slide sleeve 17. [ In this case, the end 18 may be incorporated in the drive shaft 4 or may be a separate component that is axially fixed on the drive shaft 4, for example by a snap ring .

In the case of the formation of fixed mechanical stops known in the prior art, the starting angle value is determined by the interaction of the entire drive system, since the number of constituent elements formed is large, Causing undesirable large fluctuations. Thus, for example, in a compressor equipped with a rotating ring system, the variation of the starting angular value is determined by the dimensions of the rotating ring, the dimensions of the ball joint formed between the rotating ring and the rotating pin, The dimensions of the pin, the dimensions of the drive shaft, the dimensions of the slide sleeve, the dimensions of the joint pins disposed between the slide sleeve and the swivel ring, and the dimensions of the individual components of the fixed mechanical stop. Due to the very large tolerance range, the tolerance range width of the starting angle values given from this tolerance range is correspondingly large. The large tolerance range width of the starting angular value is driven through a belt pulley in particular (but not necessarily), and in the case of a compressor with a small starting angle and a small stroke, an undesirably large fluctuation Which leads to very high power consumption, for example, in the idle state of the compressor again. In order to keep the conveying capacity of the compressor within the desired minimum range in the switched-off state, a selection part with high manufacturing accuracy can be used in connection with the measuring process which is accompanied by production, but the selection part, however, The manufacturing cost of the compressor is extremely increased.

It is an object of the present invention to provide a piston compressor of variable stroke in which a driving element, in particular a swash plate or swivel, has a minimum starting angle. In this case, the starting angle value must lie within the minimum tolerance range width, that is, when operating the compressor, for example in the idle state, the tolerance range width of the starting angle stop must be minimized to minimize power consumption. The compressor must have a simple structure of a minimum number of components in the minimum space. In addition, the minimum manufacturing, maintenance and installation costs must be required, the typical tolerance range of the components formed in the drive system can be maintained, and the use of a special selection component with the measuring process that accompanies production can be prevented have.

This problem is solved by objects having the features of the independent patent claims. Improvements are provided in the dependent patent claims.

The above problem is solved by a refrigerant compression apparatus according to the present invention having a variable stroke volume. The apparatus includes a drive shaft rotatable about a rotation axis and a drive element. Wherein the drive shaft and the drive element are mechanically coupled to each other via bolts adjusted radially to the drive shaft direction as fixed reference points on the drive shaft so that the drive elements are adjusted in a direction perpendicular to the axis of the drive shaft And is rotated together with the drive shaft. The inclination angle is variable through the slide sleeve, and the slide sleeve is disposed movably on the drive shaft in the axial direction of the drive shaft. In this case, the movement path of the slide sleeve is limited by the mechanical stop of the slide sleeve as an element for limiting the minimum stroke of the device.

According to the principles of the present invention, the mechanical stop is formed in the contact area between the slide sleeve and the bolt. The inclination angle of the driving element is limited to a minimum by using the mechanical stop for limiting the movement path of the slide sleeve. The mechanical stop is also referred to as the minimum angular stop.

The device according to the invention is preferably used in the refrigerant circulation system of the heating and cooling apparatus of the vehicle. The apparatus preferably includes a housing with at least one cylinder bore, wherein the piston is radially fixedly disposed within the at least one cylinder bore. In this case, the piston is coupled to the driving element so as to be able to move along the driving element upon rotation of the driving element, so that the rotation of the driving shaft is consequently converted into a linear reciprocating motion of the piston by the driving element. Thus, the piston compressor with a preferably variable stroke or the device formed as a belt-driven refrigerant compressor for mobility applications is driven through a clutch or through a belt pulley and therefore without a clutch.

A further preferred working example of the present invention is given by forming the slide sleeve in the form of a hollow cylinder. The slide sleeve is preferably mechanically coupled to the drive element via a joint pin.

According to one improvement of the invention, the slide sleeve comprises an opening formed radially axially and having an edge. The opening is preferably formed as an oblong hole. Alternatively, the opening may be formed in a similar form to the slot, for example a milled recess of the C-shape.

According to a preferred embodiment of the present invention, the area of the bolt protruding from the drive shaft is disposed so as to protrude through the opening of the slide sleeve. As a result, the movement path of the slide sleeve, which is movable in the axial direction of the drive shaft, The mechanical stop is limited by the opening edge of the slide sleeve with the bolt.

According to a first alternative embodiment of the invention, the mechanical stop of the slide sleeve is formed on the upper surface of the bolt as a connection between the drive shaft and the drive element.

According to a second alternative form of the invention, the bolt is arranged to fit within the through hole formed in the drive shaft and includes a fitting. In this case, the fitting protrudes from the drive shaft and is disposed on the lower surface of the bolt as a mechanical stop of the slide sleeve, wherein the lower surface of the bolt is formed as the end portion of the connection with the drive element. The fitting is preferably configured to be integrated into the bolt such that the bolt and the fitting form an integral component.

According to a further preferred embodiment of the present invention, the driving element is formed of a rotating ring. According to an alternative working example, the driving element is formed of a swash plate.

According to one improvement of the invention, a damping element is arranged in the opening edge region of the slide sleeve, where the bolt is placed in the final position of the slide sleeve. In this case, the final position of the slide sleeve means the position of the slide sleeve in which the inclination angle of the drive element is limited by the contact of the slide sleeve with the mechanical stop, that is, the bolt. The damping element absorbs the impact caused by the damping action when the slide sleeve stops at the bolt.

The refrigerant compression device according to the present invention, which has a fixed reference point in the drive shaft and has a variable stroke volume, which is formed by a fixed mechanical stop for restricting the tilt angle, has various advantages:

- the advantage that the number of components in the tolerance range is reduced to a minimum,

- The advantages of minimizing the tolerance range width given for the starting value of the tilt angle to ensure minimum power consumption in the idle state of the compressor under typical part tolerances.

- Advantages of eliminating special selective components with associated measurement processes, thereby reducing component and installation costs

Advantages of not requiring additional series elements

Further details, features and advantages of the formation examples of the present invention are set forth in the description of the following embodiments with reference to the accompanying drawings. Explanation of drawings:
1 is a cross-sectional view of a tilting plate compressor of the prior art having a variable displacement volume,
2 is a detailed view of a drive shaft with a rotor element and a swash plate of a prior art compressor, and
Figure 3 is a detail view of the arrangement of a fixed mechanical stop for a prior art compressor with a swivel or swash plate,
As a detail of the arrangement of the fixed mechanical stops for the slide sleeves of the compressors with respective swivel rings
FIGS. 4A and 4B are detailed views with fittings formed at the distal end of the bolt with reference to the joint head of the bolt,
Figures 5A and 5B are detail views according to Figures 4A and 4B with damping elements,
Figs. 6A and 6B are detailed views on the side of the joint head of the bolt, and Figs.
Figures 7a and 7b are detail views according to Figures 6a and 6b with damping elements.

Figures 4a and 4b are detailed views of the arrangement of the element 20a for limiting the minimum stroke and the element is provided with a rotating ring 5b as the fixed mechanical stop 20a of the slide sleeve 17 Is formed on the lower surface of the bolt (14) for a compressor. In the case of a compressor with a fixed reference point of the drive system in the drive shaft 4, such as a bolt 14 of a rotary-ring compressor, the fixed mechanical stop 20a of the system is fixed to the slide sleeve 17 and the bolt 14 as shown in Fig.

The bolts 14 arranged to protrude radially from the drive shaft 4 are engaged with the engagement space 16 of the rotation ring 5b opened in the direction of the drive shaft 4 using the joint head 15, And is coupled to the rotation ring 5b in this manner. The inclination angle of the rotation ring 5b can be changed through a slide sleeve 17 which is movable on the drive shaft 4 in the axial direction of the drive shaft 4 and the slide sleeve is again moved through the two joint pins 19 And is mechanically coupled to the rotation ring 5b. The rotation ring 5b is rotatably disposed in the rotation direction B about an axis vertically adjusted with respect to the drive shaft 4. [ As the slide sleeve 17 moves in the movement direction A, the rotation ring rotates in the rotation direction B.

The sliding movement of the slide sleeve 17 in the axial direction of the drive shaft 4 is limited and the inclination angle is restricted as the start angle of the rotation ring 5b with respect to the axis of the drive shaft 4, The fixed mechanical stop 20a is formed as a fitting 21 in the bolt 14. [ The fitting 21 is integrated in the bolt 14, so that the bolt 14 and the fitting 21 are formed as an integral component. The bolt 14 has a joint head 15 on one side in the axial extension which engages into the engagement space 16 of the rotation ring 5b which is open in the direction of the drive shaft 4. The joint head 15 is formed on the upper surface of the so-called bolt 14. On the other hand, and accordingly, a fitting 21 is formed at the distal end of the bolt 14 with respect to the joint head 15. The bolt 14 is disposed as a mechanical connecting element between the driving shaft 4 and the rotating ring 5b to fit into the through hole formed in the driving shaft 4. [ The bolt 14 protrudes from the drive shaft 4 using a fitting 21. The slide sleeve 17 includes an opening 22a, in particular an opening 22a formed into a slot. In the installed state of the drive system of the compressor, the region of the fitting 21 of the bolt 14 protrudes from the drive shaft 4 and extends through the opening 22a of the slide sleeve 17. The slide sleeve 17 is moved in the axial direction of the drive shaft 4 until the edge of the opening 22a of the slide sleeve 17 contacts the fitting 21 of the bolt 14, ). The movement path of the slide sleeve 17 is limited by the formation of the opening 22a together with the fitting 21 of the bolt 14. [ The edges of the slide sleeve 14, particularly the opening 22a, collide with the fitting 21 for restricting purposes. The fixed mechanical stop 20a of the starting angle between the slide sleeve 17 and the bolt 14 is formed by forming the fitting 21 on the lower surface of the bolt 14 and by the movement of the slide sleeve 17, And is pre-determined by extending the opening 22a therein.

4A, the slide sleeve 17 is brought into contact with the fitting 21 of the bolt 14, so that the rotation ring 5b is arranged at a minimum inclination angle as a start angle. As the slide sleeve 17 moves in the movement direction A1, the rotation ring 5b is inclined in the rotation direction B1. At this time, the inclination angle becomes large.

Figures 5a and 5b show a side view of the slide sleeve 17 on the underside of the bolt 14 in a compressor with a rotating ring 5b according to Figures 4a and 4b with a further formed damping element 23a. And a detailed view of the arrangement of one embodiment of the fixed mechanical stop 20a. The damping element 23a is disposed within the edge region of the opening 22a of the slide sleeve 17 so that the fitting 21 of the bolt 14 moves within the edge region when the start angle or the movement of the slide sleeve 17 And contacts the edge of the opening 22a in the case of restricting the path. The damping element 23a prevents vibration and accordingly reduces noise generation.

Figures 6a and 6b show a detailed view of the arrangement of the elements 20b for restricting the minimum stroke in the compressor with the rotation ring 5b and the fixed mechanical stop 20b of the slide sleeve 17 And is formed on the upper surface of the bolt 14. In the case of a compressor with a bolt 14 as a fixed reference point of the drive system in the drive shaft 4 the fixed mechanical stop 20b is similar to the system of Figures 4a and 4b and Figures 5a and 5b So as to be in contact with the slide sleeve (17) and the bolt (14). 4A is that the fixed mechanical stop 20b is formed on the upper surface of the bolt 14 instead of the lower surface of the bolt 14. [

In this case, the bolt 14 itself restricts the slide movement or the movement path of the slide sleeve 17 in the axial direction of the drive shaft 4, and in association with the drive shaft 4, 5b as a fixed mechanical stop portion 20b for restricting the inclination angle. The slide sleeve 17 includes an opening 22b and in particular an opening 22b formed in the slot which implements movement of the slide sleeve 17 with respect to the drive shaft 4. [ The bolt 14 protrudes from the drive shaft 4 in the direction of the joint head 15 and extends through the opening 22b formed in the slide sleeve 17. In this state, The slide sleeve 17 can move in the axial direction of the drive shaft 4, that is, in the moving direction A, until the edge of the opening 22b of the slide sleeve 17 comes into contact with the bolt 14. [ The movement path of the slide sleeve 17 is restricted by the formation of the opening 22b together with the bolt 14. [ The edges of the slide sleeve 14, particularly the opening 22b, collide with the bolt 14 for restricting purposes. The fixed mechanical stop 20b of the starting angle between the slide sleeve 17 and the bolt 14 is formed by the bolt 14 itself and by the extension of the opening 22b inside the slide sleeve 17 Is preset on the upper surface of the bolt (14).

6A, the slide sleeve 17 is brought into contact with the bolt 14, so that the rotation ring 5b is arranged at the minimum inclination angle as the start angle. As the slide sleeve 17 moves in the movement direction A1, the rotation ring 5b is inclined in the rotation direction B1. At this time, the inclination angle becomes large.

Figures 7a and 7b show a further embodiment of the invention for the slide sleeve 17 on the upper surface of the bolt 14 in a compressor with a rotating ring 5b according to Figures 6a and 6b with a further formed damping element 23b. A detailed view of the arrangement of one embodiment of the fixed mechanical stop 20b. The damping element 23b is disposed within the edge region of the opening 22b of the slide sleeve 17 so that the bolt 14 within the edge region limits the travel of the departure angle or slide sleeve 17 It is in contact with the edge of the opening 22b. The damping element 23b prevents vibration and accordingly reduces noise generation.

The fitting 21 of the bolt 14 according to Figures 4a and 4b and Figures 5a and 5b or the bolt 14 according to Figures 6a and 6b and Figures 7a and 7b itself and the respective slide sleeve 17, The number of component elements belonging to the tolerance range and the size of the tolerance range are remarkably reduced as compared with the formation example of the prior art according to Fig. 3, and as a result thereof The tolerance range width given for the starting angle value is minimized so that minimum power consumption is ensured in the idle state of the compressor under typical part tolerances.

: 각도, 경사각
min: 최소
max: 최대1: Compressor, Compressor
2: Housing
3: Piston
4: drive shaft
5: Driving element
5a: Driving element, swash plate
5b: driving element, rotating ring
6: Cylinder bore
7: Crank chamber
8: suction chamber
9: Discharge chamber
10: Belt pulley
11: Rotor element of drive shaft
12: Coupling element
13:
14: Bolt
15: Joint head
16: Coupling space
17: Slide sleeve
18: Dan
19: Joint pin
20 ', 20a, 20b: stopper, element for limiting the minimum stroke
21: fitting of the bolt 14
22a, 22b: the opening of the slide sleeve 17
23a, 23b: damping element
A, A1: the direction of movement of the slide sleeve 17
B, B1: rotation direction of the rotation ring 5b

: Angle, inclination angle
min: minimum
max: max

Claims (10)

1. A refrigerant compressor (1) having a variable displacement piston
A drive shaft 4 rotatable about a rotational axis and drive elements 5, 5a and 5b, wherein the drive shaft 4 and the drive elements 5, 5a and 5b are radially 5a and 5b are mechanically coupled to each other via a bolt 14 adjusted in the direction of the drive shaft 4 so that the drive elements 5, And the tilt angle is variable through the slide sleeve 17 and the slide sleeve is displaceable relative to the drive shaft 4 in the direction of the axis of rotation of the drive shaft 4, Wherein the movement path of the slide sleeve 17 is such that the movement path of the slide sleeve 17 is restricted by the mechanical stops 20a and 20b of the slide sleeve 17, In this case,
The mechanical stops 20a and 20b are formed in the contact area between the slide sleeve 17 and the bolt 14,
The slide sleeve (17) includes openings (22a, 22b) with an edge formed radially with respect to the axis of rotation,
The bolt 14 is arranged to fit within a through hole formed in the drive shaft 4 and includes a fitting 21 which protrudes out from the drive shaft 4 and is inserted into the slide sleeve 17 A lower surface of the bolt is formed as a distal end portion of a connection portion with the driving elements 5, 5a, 5b,
Damping elements 23a and 23b are disposed in the edge regions of the openings 22a and 22b of the slide sleeve 17 in which the bolts 14 are positioned at the final positions of the slide sleeves 17 Lt; / RTI > The method according to claim 1,
Characterized in that the slide sleeve (17) is formed in the form of a hollow cylinder. delete The method according to claim 1,
Characterized in that the openings (22a, 22b) are formed as oblong holes. The method according to claim 1,
The area of the bolt 14 protruding from the drive shaft 4 protrudes through the openings 22a and 22b of the slide sleeve 17 so that the slide sleeve 17 can be moved in the axial direction of the drive shaft 4, Characterized in that the movement path of the slide member (17) is limited by the edges of the openings (22a, 22b) of the slide sleeve (17) with the bolts (14) as mechanical stops (20a, 20b). 6. The method of claim 5,
Characterized in that the mechanical stop (20b) of the slide sleeve (17) is formed on the upper surface of the bolt (14) as a connection between the drive shaft (4) and the drive element (5) . delete The method according to claim 1,
Characterized in that the fitting (21) is formed to be integral with the bolt (14) so that the bolt (14) and the fitting (21) form an integral component. The method according to claim 1,
Characterized in that the drive element (5) is formed as a swivel (5b) or a swash plate (5a). delete

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