| 序号 | 专利名 | 申请号 | 申请日 | 公开（公告）号 | 公开（公告）日 | 发明人 |
|---|---|---|---|---|---|---|
| 41 | 具有用于转子面间隙控制的可移动端板的正排量泵组件 | CN201310225849.4 | 2013-04-28 | CN103375404A | 2013-10-30 | D·R·奥文加; B·T·史密斯 |
| 本发明涉及一种正排量泵组件，该组件包括限定转子腔的转子壳体和构造成至少部分地封闭转子腔的一端的端板。转子支承并且固定在转子轴上，转子轴延伸穿过转子腔。第一对轴承将转子轴固定到端板上。第二对轴承将转子轴到固定转子壳体上，从而防止转子轴和转子壳体之间的相对轴向运动。当转子轴由于热波动而轴向长度发生变化时，端板与转子轴一起沿轴向移动，从而减小了转子端面处的轴向间隙的变化。 | ||||||
| 42 | 单螺杆式压缩机 | CN200880122899.7 | 2008-12-26 | CN101910640B | 2013-09-25 | M·A·侯赛因; 增田正典 |
| 本发明公开了一种单螺杆式压缩机。在该单螺杆式压缩机中，由闸转子(50)和闸转子支撑部件(55)构成闸转子组装体(60)。在闸转子组装体(60)中，由闸门支撑部(57)从背面一侧支撑各个闸门(51)。在各个闸门(51)形成有沿厚度方向贯穿闸门(51)的压力导入路(52)。还有，在各个闸门(51)的背面一侧，形成有背压空间(65)。背压空间(65)经由压力导入路(52)与闸门(51)正面一侧的空间连通。为此，背压空间(65)的内压与作用在闸门(51)正面的制冷剂压力大致相等。其结果是能够抑制闸门(51)变形。 | ||||||
| 43 | 旋转式压缩机 | CN201010125935.4 | 2010-03-10 | CN102192149B | 2013-03-13 | 小津政雄; 李华明 |
| 一种旋转式压缩机，密封壳体内设置有电机部和压缩机构部，压缩机构部包括一个以上的气缸，气缸内设置有气缸压缩腔，活塞收纳在气缸压缩腔中，滑片的先端与活塞外周相接且把气缸压缩腔划分为高压腔和低压腔，曲轴与活塞相接且驱动活塞，以及用于支撑曲轴且安装于气缸上的主轴承和副轴承，主轴承与曲轴的主轴相接，副轴承与曲轴的副轴相接，其特征是在活塞的二个端部中的至少一个端部靠向其端面的位置设置有圆周槽，圆周槽的开口朝向活塞内部，圆周槽的外侧设置有弹性的薄壁；通过活塞内部与外部的压力差调整二个端部分别与主轴承和副轴承之间形成的间隙。本发明具有结构简单合理、有效降低泄漏损失、大幅度地提高压缩机的能效的特点。 | ||||||
| 44 | 涡旋压缩机 | CN201180009456.9 | 2011-02-14 | CN102753829A | 2012-10-24 | 中村壮一; 城村周一; 永原显治; 北浦洋 |
| 本发明公开了一种涡旋压缩机。与压缩途中的压缩室(25)连通的注入口(27)形成在静涡旋盘(30)上。从涡旋压缩机(10)的喷出制冷剂中分离出来的冷冻机油与中压气态制冷剂一起从注入口(27)流入压缩室(25)。在静涡旋盘(30)和动涡旋盘(40)的齿底面(31a、41a)上对着与注入口(27)连通的压缩室(25)的部分成为中间齿底区域(36、46)，比中间齿底区域(36、46)更靠近涡卷(32、42)的外周侧端部的部分成为吸入侧齿底区域(35、45)。吸入侧齿底区域(35、45)的齿底面(31a、41a)和涡卷(42、32)的顶端面(42a、32a)的间隙大于中间齿底区域(36、46)的间隙。 | ||||||
| 45 | 螺杆压缩机 | CN200880123392.3 | 2008-12-26 | CN101910641A | 2010-12-08 | 藤原秀规; 后藤英之; 宫村治则; 后藤望 |
| 本发明提供一种螺杆压缩机，其能够防止相邻两个螺旋槽同时在喷出口开口而导致的压缩机效率的降低。螺杆压缩机(1)设有螺杆转子(40)、收纳螺杆转子(40)并在内周面设置喷出口的壳体(10)以及具有与螺杆转子(40)的螺旋槽(41)啮合的闸(51、51、……)的闸转子(50)，由螺杆转子(40)、该壳体(10)以及该闸转子(50)形成的压缩室(23)压缩气体而从该喷出口喷出。喷出口分割为，当伴随螺杆转子(40)的旋转而变为螺旋槽(41)中相邻两个螺旋槽(41、41)在喷出口开口的状态时的在一方的螺旋槽(41)开口的第一口(74b)和在另一方的螺旋槽(41)开口的第二口(75b)。 | ||||||
| 46 | 螺杆式压缩机 | CN200880122453.4 | 2008-12-26 | CN101910639A | 2010-12-08 | 后藤英之; 后藤望; 藤原秀规; 宫村治则 |
| 本发明提供一种螺杆式压缩机，该螺杆式压缩机能够减少来自闸转子中的相邻齿部之间的空间的气体泄漏，从而提高压缩性能。在闸转子(3)的另一面(32)侧配置有密封部(5)。该密封部(5)堵住闸转子(3)中的相邻齿部(31)之间的空间。 | ||||||
| 47 | 单螺杆式压缩机 | CN200880102341.2 | 2008-08-07 | CN101779041A | 2010-07-14 | 宫村治则; 冈田忠司; 高桥孝幸; 大塚要; 诹佐利浩; 上野广道; 室野孝义 |
| 本发明公开了一种单螺杆式压缩机。在该单螺杆式压缩机中，闸转子(50)的闸门(51)与螺杆转子(40)的螺旋槽(41)啮合。在螺杆转子(40)的各条螺旋槽(41)中，从该各条螺旋槽(41)的起始端到压缩步骤的中途为止的区域成为吸入侧部分(45)，剩下的部分(到终止端为止的部分)成为喷出侧部分(46)。在喷出侧部分(46)，该喷出侧部分(46)的壁面(42、43、44)和闸门(51)之间的间隙实质上为零。吸入侧部分(45)的壁面(42、43、44)和闸门(51)之间的间隙，比喷出侧部分(46)的壁面(42、43、44)和闸门(51)之间的间隙宽，并且从螺旋槽(41)的起始端向终止端逐渐变窄。 | ||||||
| 48 | 油泵转子 | CN200480022947.7 | 2004-08-10 | CN100404863C | 2008-07-23 | 细野克明 |
| 本发明提供一种油泵转子，将相啮合的内转子及外转子的齿形设定为适当的形状，以实现防止油泵性能及机械效率的降低、防止噪音发生。根据本发明的油泵转子，具有齿面形状，其构成为：内转子(110)及外转子(120)中至少一个将摆线曲线二等分而分开，并以直线或曲线补充其之间的曲线。 | ||||||
| 49 | 真空泵及其起动方法 | CN03819546.1 | 2003-08-11 | CN1675469A | 2005-09-28 | 饭岛直树; 渡边二郎; 千野宏之; 柳泽清司; 川村毅 |
| 本发明涉及一种真空泵和真空泵起动方法。该真空泵包括泵转子(1)，其可旋转地安置在泵壳(2)内，以及泵转子控制器(15)，其在起动真空泵时依照预定模式控制泵转子(1)在正向或反向上旋转。 | ||||||
| 50 | Two-shaft rotary pump with escape holes | US14782735 | 2014-05-29 | US10077773B2 | 2018-09-18 | Yosuke Yoshida; Shingo Harayama; Shun Miyazawa; Humihiko Yamada |
| Provided is a two-shaft rotary pump which is capable of improving reliability and operation efficiency by preventing an exhaust gas from flowing backward into a pump as much as possible, preventing the interior of the pump form being excessively compressed as much as possible, and suppressing temperature rise in the pump. A two-shaft rotary pump in which two rotating shafts (20, 20) provided with rotors (30, 30) are supported by bearings, such that the two rotors (30, 30) are rotated in a noncontact manner with a small clearance kept therebetween and the two rotors (30, 30) are rotated in a noncontact manner with a small clearance between an inner surface of a cylinder (50) and the two rotors, and a gas sucked into the cylinder (50) and compressed is discharged from the cylinder (50), wherein an escape hole capable of letting a part of the compressed gas escape is provided in at least one of end wall portions (52) constituting both ends of the cylinder (50) and opened in the axial direction of the rotating shafts (20, 20). | ||||||
| 51 | Rotary compressor and refrigerating cycle apparatus | US14553585 | 2014-11-25 | US09879675B2 | 2018-01-30 | Kazu Takashima; Hisataka Kato; Keiichi Hasegawa; Masahiro Hatayama |
| According to one embodiment, a rotary compressor accommodating an electric motor portion and a compression mechanism portion in a sealed case, wherein the compression mechanism portion comprises a cylinder, a roller, and a vane. The vane is disposed by stacking two divided vanes in a height direction of the cylinder, which is an axis direction of the rotation axis, and where a height dimension of one divided vane is H, and a minute gap between a height dimension of the cylinder and a height dimension of the two stacked divided vanes is L, a proportion of the minute gap L to the vane height dimension H per one divided vane is 0.001 | ||||||
| 52 | CLEARANCE GAGE | US15077640 | 2016-03-22 | US20170276467A1 | 2017-09-28 | Daniel James Hassan, III; John Patrick Godsil; James Alan Davis |
| A clearance gage that includes an elongated shaft having a first end and a second end, a gage element connected to the first end of the elongated shaft, where the gage element defines a first width and a second width measured perpendicular to the elongated shaft, where the first width is larger than the second width, where a thickness of the elongated shaft is not more than the second width, where the first width defines a size of the gage element to assess a gap clearance between two components, and a marker connected to the elongated shaft, where the marker is positioned at a predetermined distance from the gage element along the elongated shaft, where the marker defines a marker width measured in a direction perpendicular to the elongated shaft that is greater than the second width of the gage element. | ||||||
| 53 | Gear pump and printing apparatus provided with same | US15095250 | 2016-04-11 | US09751321B2 | 2017-09-05 | Masaaki Ando; Noritaka Mitsuo; Norihiro Maruyama |
| A gear pump for transporting a fluid includes a pump casing; and a gear assembly which is accommodated in the pump casing. The gear assembly includes a driving gear, a driven gear that mashes with the driving gear, a driving gear shaft to which the driving gear is attached, a driven gear shaft to which the driven gear is attached, and a bearing frame that rotatably supports the driving gear shaft and rotatably supports the driven gear shaft. | ||||||
| 54 | Oil pump | US14378201 | 2013-01-29 | US09482224B2 | 2016-11-01 | Takehiko Naiki |
| An oil pump includes a housing (10, 20), a rotary shaft (30) which is supported by the housing, an inner rotor (71, 81) which is rotated in the housing integrally with the rotary shaft, an outer rotor (72, 82) which is rotated in the housing as being interlocked with the inner rotor, a rotor case (40) which is fitted into the housing and which contains the inner rotor and the outer rotor and supports an outer circumferential face of the outer rotor in a slidable manner, a side plate (50) which is arranged to be in contact with at least one annular end face of the rotor case, and an elastic member (60) which exerts an urging force to press the side plate to the annular end face of the rotor case. According to the above, slide resistance and operational torque can be reduced and constant side clearance can be maintained. | ||||||
| 55 | Scroll-Type Fluid Machine | US14652287 | 2013-12-10 | US20150322947A1 | 2015-11-12 | Kazuhiko TAKAI; Yasuomi MATSUMOTO |
| To provide a scroll-type fluid machine in which the influence on power recovery efficiency of a clearance in an expansion section is reduced. A scroll-type fluid machine (100) includes: a scroll unit (20) in which a fixed scroll (3) and an orbiting scroll (4) are disposed and an expansion section (1) and a compression section (2) are formed; and a support part (30) that supports the orbiting scroll (3) so as to be able to perform revolving motion, the compression section (2) being driven by power recovered in the expansion section (1). A minimum clearance between a wrap (3L) of the fixed scroll (3) and a wrap (4L) of the orbiting scroll (4) in the expansion section (1) is set to be less than a minimum clearance between the wrap (3L) of the fixed scroll (3) and the wrap (4L) of the orbiting scroll (4) in the compression section (2). | ||||||
| 56 | POSITIVE DISPLACEMENT PUMP ASSEMBLY WITH MOVABLE END PLATE FOR ROTOR FACE CLEARANCE CONTROL | US14398039 | 2013-04-29 | US20150118094A1 | 2015-04-30 | Daniel R. Ouwenga; Brian T. Smith |
| A positive displacement pump assembly includes a rotor housing defining a rotor cavity, and an end plate configured to at least partially close one end of the rotor cavity. Rotors are supported on and fixed to rotor shafts and extend through the rotor cavity. A first pair of bearings fixing the rotor shafts to the end plate. A second pair of bearings fixes the rotor shafts to the rotor housing, preventing relative axial movement between the rotor shafts and the rotor housing. The end plate is axially movable with the rotor shafts when the rotor shafts vary in axial length due to thermal fluctuations so that changes in an axial clearance at end faces of the rotors are reduced. | ||||||
| 57 | SCROLL COMPRESSOR | US14378844 | 2013-11-12 | US20150056091A1 | 2015-02-26 | Atsushi Sakuda; Sadayuki Yamada; Takeshi Ogata; Yusuke Imai; Hidenobu Shintaku; Takashi Morimoto |
| A diameter of a main bearing member 12m is defined as Dm, a length thereof is defined as Lm, a diameter of the eccentric bearing member 11e is defined as De and a length thereof is defined as Le. A ratio (=Lm/Dm) of the length and the diameter of the main bearing member 12m and a ratio (=Le/De) of the length and the diameter of the eccentric bearing member 11e are set to Le/De≦Lm/Dm≦1. Therefore, contact at edge portions of both ends of the eccentric bearing member 11e does not occur, and it is possible to prevent contact at edge portions of both ends of the main bearing member 12m even if the main shaft 13m inclines, and to reduce a viscosity loss caused by oil 9a. Hence, the present invention provides a scroll compressor securing reliability of the bearing members 12m, 11e and 16s and having high efficiency. | ||||||
| 58 | OIL PUMP | US14378201 | 2013-01-29 | US20150017049A1 | 2015-01-15 | Takehiko Naiki |
| An oil pump of the present invention includes a housing (10, 20), a rotary shaft (30) which is supported by the housing, an inner rotor (71, 81) which is rotated in the housing integrally with the rotary shaft, an outer rotor (72, 82) which is rotated in the housing as being interlocked with the inner rotor, a rotor case (40) which is fitted into the housing and which contains the inner rotor and the outer rotor and supports an outer circumferential face of the outer rotor in a slidable manner, a side plate (50) which is arranged to be in contact with at least one annular end face of the rotor case, and an elastic member (60) which exerts an urging force to press the side plate to the annular end face of the rotor case. According to the above, slide resistance and operational torque can be reduced and side clearance can be maintained at constant. | ||||||
| 59 | OIL PUMP ROTOR | US14236455 | 2012-12-13 | US20140178233A1 | 2014-06-26 | Atsushi Shiotani; Eiichiro Niizuma |
| Provided is an oil pump rotor capable of improving a volume efficiency and a quietness. When a diameter of a base circle bi of an inner rotor is Φ bi; a diameter of a first outer rolling circle Di is Φ Di; a diameter of a first inner rolling circle di is Φ di; a diameter of a base circle bo of an outer rotor is Φ bo; a diameter of a second outer rolling circle Do is Φ Do; a diameter of a second inner rolling circle do is Φ do; and an eccentricity amount between the inner rotor and the outer rotor is e, Φ bi=n·(Φ Di+Φ di) and Φ bo=(n+1)·(Φ Do+Φ do) hold; either Φ Di+Φ di=2e or Φ Do+Φ do=2e holds; and Φ Do>Φ Di and Φ di>Φ do hold. When a clearance between the inner rotor and the outer rotor is t, 0.3≦((Φ Do+Φ do)−(Φ Di+Φ di))·(n+1)/t≦0.6 holds, provided that Φ Di+Φ di=2e; or 0.3≦((Φ Do+Φ do)−(Φ Di+Φ di))·n/t≦0.6 holds, provided that Φ Do+Φ do=2e. | ||||||
| 60 | SCREW COMPRESSOR | US13820067 | 2011-09-29 | US20130171018A1 | 2013-07-04 | Takashi Inoue; Masanori Masuda; Hiromichi Ueno; Mohammod Anwar Hossain; Akira Matsuoka |
| A screw compressor includes a casing having low and high pressure spaces, a screw rotor inserted in a cylinder part of the casing, and a slide valve disclosed in the cylinder part. The screw rotor has a plurality of helical grooves forming a compression chamber. The slide valve is moveable along an axis of the screw rotor and faces an outer periphery of the screw rotor to form a discharge port to communicating the compression chamber with the high pressure space. Fluid in the low pressure space is sucked into the compression chamber, compressed, and then discharged to the high-pressure space when the screw rotor rotates. The slide valve includes a sealing projection located on a back surface of the slide valve opposite to the screw rotor, and separating the low and high pressure spaces from each other when the sealing projection is in slidable contact with the casing. | ||||||
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