WO2008014688A1 - Compresseur à piston rotatif - Google Patents

Compresseur à piston rotatif Download PDF

Info

Publication number
WO2008014688A1
WO2008014688A1 PCT/CN2007/002254 CN2007002254W WO2008014688A1 WO 2008014688 A1 WO2008014688 A1 WO 2008014688A1 CN 2007002254 W CN2007002254 W CN 2007002254W WO 2008014688 A1 WO2008014688 A1 WO 2008014688A1
Authority
WO
WIPO (PCT)
Prior art keywords
baffle
collar
rotor
axial
cylindrical
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2007/002254
Other languages
English (en)
French (fr)
Inventor
Xiaoying Yun
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN2006101037032A external-priority patent/CN101113735B/zh
Priority claimed from CN2006101037028A external-priority patent/CN101113734B/zh
Application filed by Individual filed Critical Individual
Priority to EP07785169.9A priority Critical patent/EP2050964B1/en
Priority to CN2007800274989A priority patent/CN101490421B/zh
Priority to US12/374,479 priority patent/US8075292B2/en
Publication of WO2008014688A1 publication Critical patent/WO2008014688A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/38—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/02 and having a hinged member
    • F01C1/39—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/02 and having a hinged member with vanes hinged to the inner as well as to the outer member

Definitions

  • the present invention relates to an energy conversion device that converts mechanical energy into pressure energy, and more particularly to a rotor compressor. Background technique
  • the existing rotor compressor has advantages that cannot be compared with other types of compressors, it has the disadvantages of complicated processing technology and unreliable sealing. Especially when the volume is increased, the reliability of the mechanical structure and the sealing is greatly reduced, so it is difficult to improve. Volumetric displacement.
  • the main reason for the above shortcomings is that the movable partitions separating the high pressure chamber and the low pressure chamber have a small range of motion and poor reliability, and the processing process is more difficult to achieve when the volumetric displacement is increased.
  • an object of the present invention is to provide a rotor compressor comprising:
  • a cylinder body comprising a cylinder body and front and rear end caps disposed on front and rear end faces of the cylinder body, the rainbow body and the front and rear end caps defining an inner cavity;
  • An eccentric rotor assembly disposed in the interior of the iris, the eccentric rotor assembly including a cylindrical rotor and a collar rotatably mounted on the cylindrical rotor, the collar being in contact with the inner wall of the cylinder, thereby forming an axially extending seal Belt
  • a chamber partitioning device for separating an axially extending sealed chamber formed between an outer peripheral surface of the eccentric rotor assembly and the inner wall surface of the rainbow into a suction chamber and a discharge chamber, wherein the suction chamber and the discharge chamber are respectively connected to the suction port and the discharge port ;
  • the chamber partitioning device comprises:
  • baffle plate having a baffle shaft disposed at an end thereof away from the eccentric rotor assembly, the cylinder main body being formed with an axially extending hole extending toward the inner cavity, the baffle shaft fitting In the hole and rotatably supported by the hole, such that the baffle can rotate within a predetermined range;
  • One of the baffle and the collar is fixedly provided with a contact element, the contact element comprises an axially extending cylindrical surface, and the other of the baffle and the collar is formed with an axial extension Arc a groove, the cylindrical surface is disposed in the arcuate groove to be in sealing contact with the circular arc groove; and the contact element and the other of the baffle and the collar are connected to each other by a connecting member
  • the connection provided by the connector allows the baffle and the collar to rotate relative to each other with the central axis of the cylindrical surface as an axis.
  • the contact element is fixedly mounted on the baffle, and an outer circumferential surface of the collar is formed with an axially extending circular arc groove.
  • the contact element is fixedly mounted on the collar, and the baffle is formed with an axially extending circular fox slot.
  • the axial end surface of the contact element is formed with an axial hole and a scalloped groove centered on the axial hole, the center of the axial hole being concentric with the center of the cylindrical surface of the contact element;
  • An axial end surface of the collar is formed with an axial hole and a groove leading to the axial hole;
  • the connecting member is U-shaped, and two leg portions thereof are respectively mounted on the axial hole of the contact element and The collar of the collar is in the axial bore, and the connection of the two legs connecting the connectors is located in the scalloped groove of the contact element and the recess of the collar.
  • the connecting member has a U shape, and two leg portions thereof are respectively installed in the axial hole of the contact member and the axial hole of the baffle, and the connection of the two leg portions connecting the connecting member The portion is located in the scalloped groove of the contact element and the groove of the baffle.
  • the suction port and the discharge port are provided on the cylinder body or on the front and rear end caps.
  • a receiving recess is formed in the inner wall of the cylinder body such that the shutter is received therein when it is pivoted to the upper position due to the rotation of the rotor assembly.
  • the discharge port is provided with a cylindrical one-way valve assembly including a cylindrical valve member for closing the outlet of the discharge chamber.
  • the rotor compressor may be of a multi-cylinder construction.
  • the arrangement of the rotors is preferably to achieve dynamic balance.
  • FIG. 1 is a cross-sectional view of a rotor compressor in accordance with a first preferred embodiment of the present invention
  • FIG. 2 is a longitudinal cross-sectional view taken along line k-k of FIG. 1;
  • Figure 3A is an axial end view of the partitioning device, and Figure 3B is a cross-sectional view taken along line B-B of Figure 3A;
  • 4A and 4B are a front view and a top view, respectively, of the connector
  • Figure 5 is an axial end view of the collar
  • Figure 6 is a cross-sectional view of a rotor compressor in accordance with a second preferred embodiment of the present invention
  • Figure 7A is an axial cross-sectional view of the cylindrical valve member
  • Figure 7A is an axial end view of the cylindrical valve member
  • Figures 8A and 8B Respectively the front view and the side view of the guide;
  • Figure 9 is an axial end view of the body of the cartridge showing the structure formed on the body of the cylinder for fitting the tubular valve assembly. Detailed description of the preferred embodiment
  • a rotor compressor according to a first preferred embodiment of the present invention includes a cylinder block 100 which is fitted from a cylindrical cylinder main body 1 to front and rear end faces of a cylinder main body 1, respectively.
  • the front end cover 13 and the rear end cover 14 are formed, and the cylinder main body 1 and the front and rear end covers 13 and 14 define an inner cavity.
  • An eccentric rotor assembly 200 is disposed in the cylinder chamber, and an axially extending sealed chamber 300 is formed between the outer peripheral surface of the eccentric rotor assembly 200 and the inner wall surface of the cylinder.
  • the eccentric rotor assembly 200 is supported on the main shaft 2 and is circumferentially positioned by the key 5.
  • the main shaft 2 is supported by bearings 15 mounted on the front and rear end covers 13 and 14.
  • the eccentric rotor assembly 200 includes a contact portion 60 that contacts the inner wall surface of the cylinder during operation thereof, and an axially extending sealing strip is formed at the contact portion.
  • the cylinder block 100 is provided with a chamber partitioning means 40 for separating the sealed chamber 300 into a suction chamber 70 and a discharge chamber 71.
  • the iris body walls on both sides of the chamber partitioning device 40 are provided with suction ports 12 and discharge ports 9 respectively communicating with the suction chamber and the discharge chamber.
  • the eccentric rotor assembly 200 includes a cylindrical rotor 4 eccentrically mounted on the main shaft 2 by a key 5, and the collar 3 is rotatably mounted on the cylindrical rotor 4. Since the collar 3 is rotatably mounted on the cylindrical rotor 4, during operation of the rotor compressor, the cylindrical rotor 4 can Rotate relative to the collar 3 and drive the collar 3 accordingly.
  • the chamber partitioning device 40 includes a baffle 8 pivotally mounted to the cylindrical body 1 by a baffle shaft 11 at one end thereof. On the other end of the baffle 8, a contact member 7 is provided which is connected to the eccentric rotor assembly 200.
  • the contact member 7 is formed with an axially extending cylindrical surface 27, and an edge is formed on the outer circumferential surface of the collar 3.
  • the axially extending circular arc groove 15 has a radius of the cylindrical surface of the contact element 7 which is substantially equal to or slightly smaller than the radius of the circular arc groove 15, so that in the assembled state, the cylindrical surface of the contact element 7 is formed on the outer circumferential surface of the collar 3 In the arcuate groove 15, a sealing contact is formed therebetween to separate the sealed chamber 300 into the suction chamber 70 and the discharge chamber 71.
  • a receiving recess 21 is formed in the inner wall of the cylinder main body 1 so that the baffle 8 and the contact member 7 are accommodated when the pivoting member 8 and the contact member 7 are pivoted to the uppermost position due to the rotation of the rotor assembly 200, thereby improving the compression of the rotor.
  • the volumetric efficiency of the machine is formed in the inner wall of the cylinder main body 1 so that the baffle 8 and the contact member 7 are accommodated when the pivoting member 8 and the contact member 7 are pivoted to the uppermost position due to the rotation of the rotor assembly 200, thereby improving the compression of the rotor. The volumetric efficiency of the machine.
  • the baffle shaft 11 is fitted in a hole 22 extending in the axis formed on the cylinder main body 1, and the side of the hole 22 facing the cylinder inner cavity is open.
  • the baffle shaft 11 is fitted in the hole 22 so as to be rotatably supported by the hole 22.
  • the baffle shaft 11 is disposed between the inner end faces of the front and rear end caps, and has no associated relationship with the end caps except for maintaining the necessary axial fit clearance with the inner end faces of the end caps.
  • the collar 3 of the eccentric rotor assembly 200 and the contact member 7 of the partitioning device 40 are connected by a connecting member 6.
  • the connecting member 6 is U-shaped and includes two cylindrical leg portions 66 and a connecting portion 65 connecting the two leg portions.
  • the contact member 7 is formed at its axial end faces with a center hole 76 for fitting a leg portion 66 of the connecting member 6.
  • a scalloped groove 75 centered on the center hole 76 is formed on both axial end faces of the contact member 7, and in the assembled state, the connecting portion 65 of the connecting member 6 is located in the scalloped groove 75 so as not to come from the contact member 7.
  • the axial end faces protrude, and the scalloped groove 75 allows the connecting member 6 (and thus the collar 3) and the contact member ⁇ (and thus the partitioning means 40) to be relatively rotated within the defined range centered on the central bore 76.
  • the circumferential dimension of the scalloped groove is so determined that, on the one hand, it should be suitably small to ensure a sealed separation between the high pressure chamber and the low pressure chamber, that is, the circumferential ends of the scalloped groove are not simultaneously connected to the high pressure chamber and the low pressure chamber. On the other hand, it should be appropriately large, and the connecting member 6 (and thus the collar 3) and the contact member 7 (and thus the separating device 40) can be relatively rotated within a desired range to achieve the intended operation of the rotor compressor.
  • the collar 3 is formed with axial holes 36 on its axially opposite end faces for fitting the other leg portion 66 of the coupling member 6. And the axial direction of the collar 3 is formed with a groove leading end faces 35 of the axial bore 36, in the assembled state, the connector connecting portion 656 is positioned within the recess 35, So as not to protrude from the axial end face of the collar 3.
  • a discharge valve assembly 10 is provided at the discharge port 9, and the valve member 10' is biased by the spring 10'' and thus closes the outlet.
  • the one-way valve assembly 10 is preferably a cylindrical valve assembly.
  • Fig. 7 shows the structure of a cylindrical valve member, wherein Fig. 7A is an axial sectional view, and Fig. 7B is an end view.
  • the cylindrical valve member 30 is a cylindrical member having a through-hole radial slit 31 formed at both axial ends thereof for receiving the cylindrical valve member.
  • the guiding portion 33 of the moving guide 32 is provided at the discharge port 9, and the valve member 10' is biased by the spring 10'' and thus closes the outlet.
  • the one-way valve assembly 10 is preferably a cylindrical valve assembly.
  • Fig. 7 shows the structure of a cylindrical valve member, wherein Fig. 7A is an axial sectional view, and Fig. 7B is an end view.
  • the cylindrical valve member 30 is a cylindrical member having a through-hole radial
  • the guide member 32 is T-shaped and includes a guiding portion 33 and a fixing portion 34 connected to the guiding portion, wherein the guiding portion 33 is adapted to be inserted into the radial slit 31 of the cylindrical valve 30 to guide Movement of the cylindrical valve member 30.
  • a T-shaped groove 40 is formed on both axial end faces of the main body 1 of the rainbow body.
  • the radially inner end of the T-shaped groove opens into the cavity 41 in which the cylindrical valve member 30 is received, and the cavity 41 is connected.
  • the hole 42 is in communication with the discharge chamber 71.
  • the radially inner end surface of the cavity 41 is formed as a cylindrical surface 43 having a radius substantially the same as the radius of the outer surface of the cylindrical valve member 30, thereby forming a mounting seat for the cylindrical valve member 30, and the communication hole 42 is formed in the cylinder On face 43.
  • the guide member 32 is fixed in position relative to the cylinder body 1 by mounting the guide member 32 in the T-shaped groove.
  • the guiding member 32 is mounted in a T-shaped groove positioned on the axial both end faces of the cylinder main body 1, and the cylindrical valve member 30 is placed in the mounting seat in the form of a cylindrical surface 43, and the guiding member 32 is guided.
  • the overhanging portion of the lead portion 33 is inserted into the radial slit 31 of the cylindrical valve member 30; at the same time, the cylindrical valve member 30 is closed by the biasing of the spring (not shown) to close the communication hole 42.
  • the cylindrical valve member 30 described above is a cylindrical member, but it is obvious that it can also be constructed as a solid cylindrical member.
  • the eccentric rotor assembly 200 when the eccentric rotor assembly 200 is rotated clockwise under the driving of the main shaft 1, the volume in the suction chamber 70 is increased to form a negative pressure, and the gas or liquid is drawn into the cylinder through the suction port 12 communicating with the suction chamber.
  • the gas or liquid in the discharge chamber 71 is pressed in accordance with the clockwise movement of the contact portion 60, thereby being discharged through the discharge port 9 communicating with the discharge chamber.
  • the separating device ensures that the cylindrical surface of the contact element 7 always maintains good contact with the circular arc groove 15 on the collar 3 by the pressure difference between the connecting device 6 and the suction chamber 70 and the discharge chamber 71, thereby achieving oil inlet.
  • the rotor compressor of the second preferred embodiment is substantially identical in construction to the rotor compressor of the first preferred embodiment, except for the structure of the partitioning device 40.
  • the contact member 7' having a cylindrical surface is fixed to the collar 3 of the eccentric rotor assembly 200, and is formed on the side of the shutter 8 facing the collar 3.
  • a sealing contact is formed therebetween to separate the sealed chamber 300 into the suction chamber 70 and the discharge chamber 71.
  • the contact member 7' and the shutter 8 fixed to the collar 3 are connected by a connecting member 6.
  • the contact member 7' is formed with a center hole on both axial end faces thereof for fitting a leg portion 66 of the connecting member 6.
  • a scalloped groove centered on the central hole is formed on both axial end faces of the contact member 7'.
  • the connecting portion 65 of the connecting member 6 is located in the scalloped groove so as not to be axially from the contact member 7'
  • the end faces protrude, and the scalloped recess allows the connecting member 6 (and thus the separating means) and the contact member (and thus the collar) to rotate relative to each other within the defined range centered on the central bore.
  • the circumferential dimension of the scalloped groove is so determined that, on the one hand, it should be suitably small to ensure a sealed separation between the high pressure chamber and the low pressure chamber, that is, the circumferential ends of the scalloped groove are not simultaneously connected to the high pressure chamber and the low pressure chamber. On the other hand, it should be appropriately large, and the connecting member 6 (and thus the separating means) and the contact member (and thus the collar) can be relatively rotated within a desired range to achieve the intended operation of the rotor compressor.
  • the baffle 8 is formed with axial holes on its axially opposite end faces for fitting the other leg portion 66 of the connecting member 6. Further, grooves are formed on the axial end faces of the baffle plate 8 to the axial holes. In the assembled state, the connecting portion 65 of the connecting member 6 is located in the recess so as not to protrude from the axial end surface of the baffle 8.
  • the suction port 12 and the discharge port 9 are respectively provided on the circumferential wall of the cylinder main body 1, but the suction port 12 and the discharge port 9 may be respectively provided on the front and rear end covers of the rainbow body.
  • the contact member 7 and the collar 3 or the contact member 7' and the baffle 8 are connected at both axial ends by means of two connecting members, and it is obvious that only one connecting member can be used to realize the Said the connection. Moreover, the contact element 7 and the collar 3 or the connection between the contact element 7' and the baffle 8
  • the manner of connection is also not limited to the particular manner illustrated, and any other means of connection that can achieve the same function are also possible.
  • the baffle 8, the baffle shaft 11, and the contact member 7 are integrally formed with each other, but the baffle 8, the baffle shaft 11, and the contact member 7 may be separate members from each other and fixed to each other.
  • the partitioning device 40 is constructed.
  • the present invention has been described by taking a single-cylinder rotor compressor as an example, but it will be apparent to those skilled in the art that the present invention is equally applicable to a multi-cylinder rotor compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Description

4 转子压缩机
所属技术领域
本发明涉及一种将机械能转变为压力能的能量转换装置，特别是一种转 子压缩机。 背景技术
现有转子压缩机尽管具有其他种类压缩机无法比拟的优点，但由于存在 着加工工艺复杂、 密封不可靠的缺点， 尤其在容积加大时机械结构和密封的 可靠性大为降低， 因此难于提高容积排量。 造成上述缺点的主要原因在于分 隔高压腔与低压腔的活动的分隔挡块活动范围小、 可靠性较差， 当实现增大 容积排量时， 加工工艺更加难以实现。 技术解决方案
鉴于此， 本发明的目的是提供一种转子压缩机， 包括：
缸体， 该缸体包括缸体主体以及设置在缸体主体前后端面上的前后端 盖， 所述虹体主体和前后端盖限定一内腔；
配置在虹体内腔中的偏心转子组件，偏心转子组件包括圆柱形转子以及 可转动地安装在圆柱形转子上的套环， 所述套环与缸体内壁接触， 借此形成 轴向延伸的密封带；
主轴， 圆柱形转子安装在主轴上并可随之一同旋转；
腔室分隔装置，用于将偏心转子组件外周面与虹体内壁面间形成的轴向 延伸的密封腔室分隔为吸入腔和排出腔， 所述吸入腔和排出腔分别与吸入口 和排出口连通；
其中所述腔室分隔装置包括：
挡板， 所述挡板在其背离偏心转子组件的一端设置有挡板轴， 所述缸体 主体上形成有一轴向延伸的、 朝向所述内腔敞开的孔， 所述挡板轴配装在所 述孔中并由该孔可转动地支撑， 使得挡板可在预定范围内转动；
所述挡板和所述套环之一上固定装设有接触元件，该接触元件包括轴向 延伸的圓柱面， 而所述挡板和所述套环中的另一个上形成有轴向延伸的圆弧 槽， 所述圆柱面配设在所述圓弧槽中而与所述圆弧槽密封接触； 所述接触元件与所述挡板和所述套环中的所述另一个利用连接件彼此 连接， 由所述连接件提供的连接允许所述挡板和所述套环以所述圓柱面的中 心轴线为轴线相对彼此^转。
优选地， 所述接触元件固定装设于所述挡板， 所述套环的外圓周面上形 成有轴向延伸的圆弧槽。
优选地， 所述触元件固定装设于所述套环， 所述挡板上形成有轴向延伸 的圆狐槽。
优选地，所述接触元件的轴向端面上形成有轴向孔以及以所述轴向孔为 中心的扇形凹槽， 所述轴向孔的中心与所述接触元件的圆柱面的中心同心； 所述套环的轴向端面上形成有轴向孔以及通向该轴向孔的凹槽； 所述连接件 呈 U形，其两个腿部分别安装于所述接触元件的轴向孔和所述套环的轴向孔 中， 而连接所述连接件的所述两个腿部的连接部位于所述接触元件的扇形凹 槽和所述套环的凹槽中。 中心的扇形凹槽， 所述轴向孔的中心与所述接触元件的圆柱面的中心同心； 所述挡板的轴向端面上形成有轴向孔以及通向该轴向孔的凹槽； 所述连接件 呈 U形，其两个腿部分别安装于所述接触元件的轴向孔和所述挡板的轴向孔 中 , 而连接所述连接件的所述两个腿部的连接部位于所述接触元件的扇形凹 槽和所述挡板的凹槽中。
优选地， 所述吸入口和排出口设置在所述缸体主体上或前后端盖上。 优选地， 于缸体主体的内壁上形成有一容放凹槽， 使得挡板在其由于转 子组件的转动枢转至上部位置时容放其中。
优选地， 所述排出口设置有筒形单向阀组件， 该筒形单向阀组件包括用 以将排出腔的出口封闭的筒形阀件。
才艮据本发明另一方面， 转子压缩机可以是多缸结构。 在多缸结构中， 各 转子的排布以实现动平衡为宜。
由于本发明所采用的分隔装置，使得转子压缩机的容积效率得以大大提 高， 结构更加简单， 工艺性更优越， 机械运动的条件尤其合理， 可进一步实 现低噪声、 无震动。 附图的简要说明
下面结合附图和实施例对本发明作进一步详细说明， 其中
图 1是根据本发明第一优选实施例的转子压缩机的横剖面视图； 图 2是沿图 1中的 k-k线截取的纵向剖面视图；
图 3A是分隔装置的轴向端视图， 图 3B是沿图 3A中的 B- B线截取的剖 面视图；
图 4A和 4B分別是连接件的主视图和俯视图；
图 5是套环的轴向端视图；
图 6是根据本发明第二优选实施例的转子压缩机的横剖面视图； 图 7A是筒形阀件的轴向剖面视图， 图 7A是筒形阀件的轴向端视图； 图 8A和 8B分别是导引件的主视图和侧视图； 以及
图 9是鉦体主体的轴向端视图，示出了于缸体主体上形成的用于配装筒 形阀组件的结构。 优选实施例的详细说明
下面参照图 1和图 2, 它们分別为本发明第一优选实施例的转子压缩机 的横向剖面视图和纵向剖面视图。
如图 1和 2所示，根据本发明第一优选实施例的转子压缩机包括有缸体 100,虹体 100由圆筒形缸体主体 1、分别配装在缸体主体 1前后端面上的前 端盖 13和后端盖 14构成， 缸体主体 1与前、 后端盖 13和 14限定一内腔。
缸体内腔中装有偏心转子组件 200, 偏心转子组件 200的外周面与缸体 内壁面之间形成一轴向延伸的密封腔室 300。 偏心转子组件 200支承在主轴 2上并通过键 5周向定位。 主轴 2通过装设在前、 后端盖 13和 14上的轴承 15予以支撑。偏心转子组件 200包括在其运转过程中与缸体内壁面接触的接 触部位 60， 于该接触部位处形成一轴向延伸的密封带。
缸体 100上设置有一将密封腔室 300分隔为吸入腔 70和排出腔 71的腔 室分隔装置 40。 腔室分隔装置 40两侧的虹体壁上开设有分别与吸入腔和排 出腔连通的吸入口 12和排出口 9。
如图 1和 2所示，偏心转子组件 200包括通过键 5偏心安装在主轴 2上 的圆柱形转子 4 , 套环 3可转动地安装在圆柱形转子 4上。 由于套环 3可相 对转动地安装在圆柱形转子 4上， 在转子压缩机操作期间， 圆柱形转子 4可 相对于套环 3转动并相应地驱动套环 3。
腔室分隔装置 40包括挡板 8 , 挡板 8通过位于其一端的挡板轴 11枢转 安装在圆筒形^:体主体 1上。在挡板 8的另一端部上设置有与偏心转子组件 200接处的接触元件 7 , 接触元件 7上形成有轴向延伸的圆柱面 27 , 而在套 环 3的外圆周面上形成有沿轴向延伸的圆弧槽 15 ,接触元件 7圓柱面的半径 基本上等于或略小于圆弧槽 15的半径， 从而在组装状态下， 接触元件 7圆 柱面位于套环 3外圓周面上形成的圆弧槽 15中，且两者之间形成密封接触， 用以将密封腔室 300分隔为吸入腔 70和排出腔 71。
此外， 于缸体主体 1的内壁上形成有一容放凹槽 21，使得当挡板 8和接 触元件 7由于转子组件 200的转动枢转至最上部位置时容放其中， 由此可提 高转子压缩机的容积效率。
挡板轴 11配装在于缸体主体 1上形成的轴线延伸的孔 22中， 孔 22的 朝向缸体内腔的一侧敞开。 挡板轴 11配装在孔 22中， 从而由孔 22可转动 地支撑。 挡板轴 11 配置在前后端盖的内端面之间， 其除了与端盖的内端面 保持必要的轴向配合间隙外， 与端盖没有任何关联。
如图 1所示，通过连接件 6连接偏心转子组件 200的套环 3与分隔装置 40的接触元件 7。 如图 4A和 4B所示， 连接件 6呈 U形， 包括两个圆柱形腿 部 66以及连接两个腿部的连接部 65。
如图 3所示，接触元件 7在其轴向两端面上形成有中心孔 76 ,该中心孔 76用于配装连接件 6的一个腿部 66。 且在接触元件 7轴向两端面上形成有 以中心孔 76为中心的扇形凹槽 75 , 在组装状态下， 连接件 6的连接部 65 位于扇形凹槽 75内， 以便不从接触元件 7的轴向端面突出， 扇形凹槽 75允 许连接件 6 (从而套环 3 )和接触元件 Ί (从而分隔装置 40 )以中心孔 76为 中心在其所限定的范围内相对转动。 扇形凹槽的周向尺寸如此确定， 使得一 方面， 它应当适当小而保证高压腔和低压腔之间实现密封分隔， 即不会出现 扇形凹槽周向两端同时与高压腔和低压腔连通的情况； 另一方面它应当适当 大， 而能够使连接件 6 (从而套环 3 )和接触元件 7 (从而分隔装置 40 )在 预期的范围内相对转动以实现转子压缩机的预期操作。
如图 5所示， 套环 3在其轴向两端面上形成有轴向孔 36, 该轴向孔 36 用于配装连接件 6的另一个腿部 66。且在套环 3轴向两端面上形成有通向轴 向孔 36的凹槽 35 , 在组装状态下， 连接件 6的连接部 65位于凹槽 35内， 以便不从套环 3轴向端面突出。
如图 1所示， 排出口 9处设置有单向阀組件 10 , 阀件 10'受弹簧 10' '的 偏压， 并因此将出口封闭。 单向阀组件 10优选地是筒形阀组件。 图 7示出 了筒形阀件的结构， 其中图 7A是轴向剖面视图， 而图 7B是端视图。 如图 7A和 7B所示， 筒形阀件 30为一圆筒形件， 于其轴向两端处分别形成有贯 通的径向切口 31 , 该切口用于装放用于引导筒形阀件移动的导引件 32的导 引部 33。
图 8A和 8B分别示出了导引件 32的主视图和侧视图。 如图 8所示， 导 引件 32呈 T形， 包括导引部 33和与导引部连接的固定部 34, 其中导引部 33适于插入筒形阀 30的径向切口 31中以引导筒形阀件 30的移动。
如图 9所示， 于虹体主体 1的轴向两端面上形成有 T形槽 40 , T形槽的 径向内端通向筒形阀件 30容放其中的腔 41 , 腔 41经由连通孔 42与排出腔 71连通。 腔 41的径向内端表面形成为圆柱面 43， 该圆柱面 43的半径与筒 形阀件 30外表面的半径基本相同， 从而形成筒形阀件 30的安装座， 连通孔 42形成在圆柱面 43上。 通过将导引件 32安装于该 T形槽中， 将导引件 32 相对于缸体主体 1固定就位。
在组装状态下， 导引件 32安装定位于缸体主体 1轴向两端面上的 T形 槽中， 筒形阀件 30安放在圆柱面 43形式的安装座中， 而导引件 32的导引 部 33的外伸部分插入筒形阀件 30径向切口 31中； 同时， 筒形阀件 30籍由 弹簧（图中未示） 的偏压将连通孔 42封闭。
上面所述的筒形阀件 30为圆筒形件， 但显而易见的是， 其也可以构作 成实心的圆柱形件。
下面结合附图说明本发明转子压缩机的操作。
如图 1所示， 当偏心转子组件 200在主轴 1的驱动下沿顺时针旋转时， 吸入腔 70 中体积增大而形成负压， 于是气体或液体经由与吸入腔连通的吸 入口 12吸入缸内； 同时， 排出腔 71中的气体或液体随着接触部位 60的顺 时针运动而受压， 从而经由与排出腔连通的排出口 9排出。 而分隔装置籍由 连接装置 6以及吸入腔 70与排出腔 71之间的压差作用确保接触元件 7的圆 柱面始终与套环 3上的圆弧槽 15保持良好的接触状态， 从而实现进油腔和 排出腔之间良好的密封， 以使上述动作得以发生。 随着转子组件的转动， 上 述过程不断重复进行。 下面结合附图 6说明本发明笫二优选实施例的转子压缩机。第二优选实 施例的转子压缩机与第一优选实施例的转子压缩机结构上基本相同， 区別在 于分隔装置 40的结构。
如图 6所示， 在本发明第二优选实施例中， 具有圓柱表面的接触元件 7' 固定于偏心转子组件 200的套环 3, 而在挡板 8的面对套环 3的一侧形成有 沿轴向延伸的圆弧槽 15'， 接触元件 7'圆柱面的半径基本上等于或略小于圆 弧槽 15'的半径， 从而在组装状态下， 接触元件 7'圆柱面位于挡板 8上形成 的圓弧槽 15'中， 且两者之间形成密封接触， 用以将密封腔室 300分隔为吸 入腔 70和排出腔 71。
类似于第一实施例（参见图 3-5 ),通过连接件 6连接固定于套环 3的接 触元件 7'和挡板 8。 接触元件 7'在其轴向两端面上形成有中心孔， 该中心孔 用于配装连接件 6的一个腿部 66。且在接触元件 7'轴向两端面上形成有以中 心孔为中心的扇形凹槽， 在组装状态下， 连接件 6的连接部 65位于扇形凹 槽内， 以便不从接触元件 7'轴向端面突出，扇形凹槽允许连接件 6 (从而分隔 装置）和接触元件（从而套环） 以中心孔为中心在其所限定的范围内相对转 动。 扇形凹槽的周向尺寸如此确定， 使得一方面， 它应当适当小而保证高压 腔和低压腔之间实现密封分隔， 即不会出现扇形凹槽周向两端同时与高压腔 和低压腔连通的情况； 另一方面它应当适当大， 而能够使连接件 6 (从而分隔 装置）和接触元件（从而套环）在预期的范围内相对转动以实现转子压缩机 预期操作。
挡板 8在其轴向两端面上形成有轴向孔，该轴向孔用于配装连接件 6的 另一个腿部 66。且在挡板 8轴向两端面上形成有通向轴向孔的凹槽，在组装 状态下， 连接件 6的连接部 65位于凹槽内， 以便不从挡板 8轴向端面突出。
以上结合附图和实施例对本发明进行了说明，但本领域技术人员应当理 解， 上述实施例仅是例示性的而非限制性的， 在不背离本发明的精神和范围 的条件下， 可对上述实施例作出种种改进。
例如，在上面的实施例中，吸入口 12和排出口 9分别设置在缸体主体 1 的圆周壁上， 但吸入口 12和排出口 9也可分别设置在虹体的前后端盖上。
在上面的实施例中，利用两个连接件于轴向两端来连接接触元件 7和套 环 3或接触元件 7'和挡板 8 , 显而易见的是， 也可以仅只采用一个连接件来 实现所述连接。 而且， 接触元件 7和套环 3或接触元件 7'和挡板 8之间的连 接方式也不限于所说明的特定方式，可实现相同功能的任何其他连接方式也 是可行的。
在上面的第一实施例中，挡板 8、挡板轴 11以及接触元件 7彼此一体形 成， 但挡板 8、挡板轴 11以及接触元件 7可以是彼此独立的部件，彼此固定 在一起而构成分隔装置 40。
在上面的实施例中， 以单缸转子压缩机为例对本发明进行了说明， 但对 业内人士而言显而易见的是， 本发明同样适用于多缸转子压缩机。

Claims

权利要求
1. 一种转子压缩机， 包括：
缸体， 该缸体包括缸体主体以及设置在虹体主体前后端面上的前后端 盖， 所述虹体主体和前后端盖限定一内腔；
配置在缸体内腔中的偏心转子组件，偏心转子組件包括圆柱形转子以及 可转动地安装在圆柱形转子上的套环， 所述套环与缸体内壁接触， 借此形成 轴向延伸的密封带；
主轴， 圆柱形转子安装在主轴上并可随之一同旋转；
腔室分隔装置，用于将偏心转子组件外周面与缸体内壁面间形成的轴向 延伸的密封腔室分隔为吸入腔和排出腔， 所述吸入腔和排出腔分别与吸入口 和排出口连通；
其中所述腔室分隔装置包括：
挡板， 所述挡板在其背离偏心转子组件的一端设置有挡板轴， 所述缸体 主体上形成有一轴向延伸的、 朝向所述内腔敞开的孔， 所述挡板轴配装在所 述孔中并由该孔可转动地支撑， 使得挡板可在预定范围内转动；
所述挡板和所述套环之一上固定装设有接触元件，该接触元件包括轴向 延伸的圆柱面， 而所述挡板和所述套环中的另一个上形成有轴向延伸的圆弧 槽， 所述圆柱面配设在所述圆弧槽中而与所述圆弧槽密封接触；
所述接触元件与所述挡板和所述套环中的所述另一个利用连接件彼此 连接， 由所述连接件提供的连接允许所述挡板和所述套环以所述圓柱面的中 心轴线为轴线相对彼此 4区转。
2. 如权利要求 1所述的转子压缩机， 其中， 所述接触元件固定装设于 所述挡板， 所述套环的外圆周面上形成有轴向延伸的圆弧槽。
3. 如权利要求 1所述的转子压缩机， 其中， 所述接触元件固定装设于 所述套环， 所述挡板上形成有轴向延伸的圆弧槽。
4. 如权利要求 2所述的转子压缩机， 其中， 所述接触元件的轴向端面 上形成有轴向孔以及以所述轴向孔为中心的扇形凹槽， 所述轴向孔的中心与 所述接触元件的圆柱面的中心同心 ,
所述套环的轴向端面上形成有轴向孔以及通向该轴向孔的凹槽， 所述连接件呈 U形，其两个腿部分别安装于所述接触元件的轴向孔和所 述套环的轴向孔中， 而连接所述连接件的所述两个腿部的连接部位于所述接 触元件的扇形凹槽和所述套环的凹槽中。
5. 如权利要求 3所述的转子压缩机， 其中， 所述接触元件的轴向端面 上形成有轴向孔以及以所述轴向孔为中心的扇形凹槽， 所述轴向孔的中心与 所述接触元件的圆柱面的中心同心， 所述连接件呈 U形，其两个腿部分别安装于所述接触元件的轴向孔和所 述挡板的轴向孔中， 而连接所述连接件的所述两个腿部的连接部位于所述接 触元件的扇形凹槽和所述挡板的凹槽中。
6. 如权利要求 1所述的转子压缩机， 其中， 所述吸入口和排出口设置 在所述虹体主体上或前后端盖上。
7. 如权利要求 1所述的转子压缩机， 其中， 于缸体主体的内壁上形成 有一容放凹槽，使得挡板在其由于转子组件的转动枢转至上部位置时容放其 中。
8. 如权利要求 1所述的转子压缩机， 其中， 所述排出口设置有筒形单 向阀组件， 该筒形单向阀组件包括用以将排出腔的出口封闭的筒形阔件。
9. 如权利要求 1所述的转子压缩机， 其中， 包括有多个沿轴向排列的 缸。
10. 如权利要求 9所述的转子压缩机， 其中， 各缸中转子的相位角等于 360° 除以缸数。
PCT/CN2007/002254 2006-07-26 2007-07-25 Compresseur à piston rotatif Ceased WO2008014688A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP07785169.9A EP2050964B1 (en) 2006-07-26 2007-07-25 A rotary piston compressor
CN2007800274989A CN101490421B (zh) 2006-07-26 2007-07-25 转子压缩机
US12/374,479 US8075292B2 (en) 2006-07-26 2007-07-25 Eccentric rotor compressor

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN200610103702.8 2006-07-26
CN200610103703.2 2006-07-26
CN2006101037032A CN101113735B (zh) 2006-07-26 2006-07-26 一种转子压缩机
CN2006101037028A CN101113734B (zh) 2006-07-26 2006-07-26 转子式压缩机

Publications (1)

Publication Number Publication Date
WO2008014688A1 true WO2008014688A1 (fr) 2008-02-07

Family

ID=38996873

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2007/002254 Ceased WO2008014688A1 (fr) 2006-07-26 2007-07-25 Compresseur à piston rotatif

Country Status (3)

Country Link
US (1) US8075292B2 (zh)
EP (1) EP2050964B1 (zh)
WO (1) WO2008014688A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117212160A (zh) * 2023-09-14 2023-12-12 珠海凌达压缩机有限公司 一种压缩结构及压缩机

Families Citing this family (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8075668B2 (en) 2005-03-29 2011-12-13 Dresser-Rand Company Drainage system for compressor separators
EP2063978B1 (en) 2006-09-19 2014-07-09 Dresser-Rand Company Rotary separator drum seal
CA2663531C (en) 2006-09-21 2014-05-20 William C. Maier Separator drum and compressor impeller assembly
WO2008039733A2 (en) 2006-09-25 2008-04-03 Dresser-Rand Company Compressor mounting system
MX2009003175A (es) 2006-09-25 2009-04-03 Dresser Rand Co Cubierta de acceso para bobina conectora presurizada.
BRPI0717087B1 (pt) 2006-09-25 2018-10-16 Dresser Rand Co sistema de carretel conector para conectar um primeiro componente e um segundo componente de um sistema de compressão industrial
WO2008039446A2 (en) 2006-09-25 2008-04-03 Dresser-Rand Company Fluid deflector for fluid separator devices
CA2663883C (en) 2006-09-25 2015-02-03 Kevin M. Majot Coupling guard system
EP2415507A1 (en) 2006-09-26 2012-02-08 Dresser-Rand Company Improved static fluid separator device
WO2009111616A2 (en) 2008-03-05 2009-09-11 Dresser-Rand Company Compressor assembly including separator and ejector pump
US8062400B2 (en) 2008-06-25 2011-11-22 Dresser-Rand Company Dual body drum for rotary separators
US8079805B2 (en) 2008-06-25 2011-12-20 Dresser-Rand Company Rotary separator and shaft coupler for compressors
US7922218B2 (en) 2008-06-25 2011-04-12 Dresser-Rand Company Shear ring casing coupler device
US8210804B2 (en) 2009-03-20 2012-07-03 Dresser-Rand Company Slidable cover for casing access port
US8087901B2 (en) 2009-03-20 2012-01-03 Dresser-Rand Company Fluid channeling device for back-to-back compressors
US8061972B2 (en) 2009-03-24 2011-11-22 Dresser-Rand Company High pressure casing access cover
US8414692B2 (en) 2009-09-15 2013-04-09 Dresser-Rand Company Density-based compact separator
US9095856B2 (en) 2010-02-10 2015-08-04 Dresser-Rand Company Separator fluid collector and method
WO2012009158A2 (en) 2010-07-15 2012-01-19 Dresser-Rand Company Enhanced in-line rotary separator
US8663483B2 (en) 2010-07-15 2014-03-04 Dresser-Rand Company Radial vane pack for rotary separators
US8657935B2 (en) 2010-07-20 2014-02-25 Dresser-Rand Company Combination of expansion and cooling to enhance separation
US8821362B2 (en) 2010-07-21 2014-09-02 Dresser-Rand Company Multiple modular in-line rotary separator bundle
JP5936144B2 (ja) 2010-09-09 2016-06-15 ドレッサー ランド カンパニーＤｒｅｓｓｅｒ−Ｒａｎｄ Ｃｏｍｐａｎｙ 洗浄可能に制御された排水管
EP2659277B8 (en) 2010-12-30 2018-05-23 Dresser-Rand Company Method for on-line detection of resistance-to-ground faults in active magnetic bearing systems
US8994237B2 (en) 2010-12-30 2015-03-31 Dresser-Rand Company Method for on-line detection of liquid and potential for the occurrence of resistance to ground faults in active magnetic bearing systems
US9551349B2 (en) 2011-04-08 2017-01-24 Dresser-Rand Company Circulating dielectric oil cooling system for canned bearings and canned electronics
US8876389B2 (en) 2011-05-27 2014-11-04 Dresser-Rand Company Segmented coast-down bearing for magnetic bearing systems
US8851756B2 (en) 2011-06-29 2014-10-07 Dresser-Rand Company Whirl inhibiting coast-down bearing for magnetic bearing systems
CN103615389B (zh) * 2013-12-06 2016-08-17 西南石油大学 一种偏心转子油气混输泵
CN103867440B (zh) * 2014-03-28 2016-04-20 袁政 压缩机

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2242708A (en) * 1990-04-04 1991-10-09 Pierburg Gmbh Sliding-vane or swing-vane vacuum pump
SU1779786A1 (ru) * 1989-08-25 1992-12-07 Izmalkov German Potophaя maшиha
RU2103553C1 (ru) * 1994-08-31 1998-01-27 Научно-производственное управление акционерного общества "Оренбургнефть" Насос
WO1999058855A1 (fr) * 1998-05-08 1999-11-18 Xiaoying Yun Pompe a piston rotatif
CN1263292A (zh) * 1999-01-25 2000-08-16 富士通株式会社 用于电子硬件的功能扩展装置
WO2001073266A1 (fr) * 2000-03-27 2001-10-04 Marcel Mille Machine motrice et receptrice a mouvement rotatif
US20040071577A1 (en) * 2001-04-12 2004-04-15 Erich Becker Rotary compressor
CN1707110A (zh) * 2004-06-11 2005-12-14 云晓璎 转子泵

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1012237A (en) * 1911-06-02 1911-12-19 William M Flagg Rotary pump.
GB150943A (en) * 1920-02-11 1920-09-16 Recip Roto Engine Company Improvements in rotary pumps and engines
US1681583A (en) * 1926-03-29 1928-08-21 Guttner Georg Rotary motor or compressor
US2094525A (en) * 1935-11-26 1937-09-28 Calling John Rotary compressor
US2238395A (en) * 1939-02-13 1941-04-15 Nittka Alfred Pump
FR1341348A (fr) * 1962-12-19 1963-10-25 Pompe à fluides
GB1085542A (en) * 1966-11-18 1967-10-04 William Edgar Storey Improvements in or relating to rotary-piston machines of the hinged abutment type
CH657665A5 (en) * 1980-10-16 1986-09-15 Peter Stillhart Fa Rotary piston engine
US4423710A (en) * 1981-11-09 1984-01-03 Williams Robert H High compression rotary engine
CN1078680C (zh) 1999-01-26 2002-01-30 付云树 圆弧铰接隔离叶片滚动转子压缩机
CN1482362A (zh) * 2003-02-12 2004-03-17 一种转子泵

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU1779786A1 (ru) * 1989-08-25 1992-12-07 Izmalkov German Potophaя maшиha
GB2242708A (en) * 1990-04-04 1991-10-09 Pierburg Gmbh Sliding-vane or swing-vane vacuum pump
RU2103553C1 (ru) * 1994-08-31 1998-01-27 Научно-производственное управление акционерного общества "Оренбургнефть" Насос
WO1999058855A1 (fr) * 1998-05-08 1999-11-18 Xiaoying Yun Pompe a piston rotatif
CN1263292A (zh) * 1999-01-25 2000-08-16 富士通株式会社 用于电子硬件的功能扩展装置
WO2001073266A1 (fr) * 2000-03-27 2001-10-04 Marcel Mille Machine motrice et receptrice a mouvement rotatif
US20040071577A1 (en) * 2001-04-12 2004-04-15 Erich Becker Rotary compressor
CN1707110A (zh) * 2004-06-11 2005-12-14 云晓璎 转子泵

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2050964A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117212160A (zh) * 2023-09-14 2023-12-12 珠海凌达压缩机有限公司 一种压缩结构及压缩机

Also Published As

Publication number Publication date
US8075292B2 (en) 2011-12-13
EP2050964A4 (en) 2014-12-10
EP2050964A1 (en) 2009-04-22
US20090169407A1 (en) 2009-07-02
EP2050964B1 (en) 2017-03-29

Similar Documents

Publication Publication Date Title
WO2008014688A1 (fr) Compresseur à piston rotatif
CN101490421B (zh) 转子压缩机
CN104160154A (zh) 卧式涡旋压缩机
WO2004072482A1 (fr) Pompe a rotor
KR20050011523A (ko) 용량가변 회전압축기
WO2011072617A1 (zh) 全封闭式制冷压缩机及其转子压缩机单元
KR20060024934A (ko) 다기통 회전압축기
WO1999058855A1 (fr) Pompe a piston rotatif
WO2013152706A1 (zh) 转子泵以及包括转子泵的旋转机械
JPH06173865A (ja) スクロール型圧縮機
EP4151833B1 (en) Rotary compressor
JP2011214482A (ja) ロータリ圧縮機
CN100410539C (zh) 可变容量旋转压缩机
US11415132B2 (en) Scroll compressor containing scroll self-rotation prevention arrangement
CN100545459C (zh) 可变容量旋转式压缩机
CN212106256U (zh) 叶片回转式压缩机
JP2022114854A (ja) スクロール型圧縮機
CN117917505A (zh) 涡旋型压缩机
KR20190000688A (ko) 토출 성능을 개선한 압축기
EP4177469B1 (en) Rotary compressor
KR20190114735A (ko) 압축기
JP2005226607A (ja) ベーンポンプ
CN119288868A (zh) 一种电机外置泵体结构及具有其的压缩机
KR100521097B1 (ko) 용량가변 회전압축기
KR20020078790A (ko) 압축기의 마찰 저감 장치

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 200780027498.9

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 07785169

Country of ref document: EP

Kind code of ref document: A1

DPE1 Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101)
WWE Wipo information: entry into national phase

Ref document number: 12374479

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

NENP Non-entry into the national phase

Ref country code: RU

REEP Request for entry into the european phase

Ref document number: 2007785169

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2007785169

Country of ref document: EP